JP2000283571A - Refrigeration air-conditioning device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress the variations in refrigerating cycles that are generated when a compressor which is capable of operating at gradiational capacities is operated at a continuous capacity without using an inverter. SOLUTION: At least one compressor 1a which is capable of operating at gradiational capacities and at least one compressor 1b which operates at a fixed capacity are provided, and the compressor 1a is operated at a different stage of capacity for each period of short time allocated by time distribution. The time allocation and the mean capacity in a short period are changes, and the entire operation capacity of a plurality of compressor 1a and 1b is made continuously variable. Moreover, the short period of time allocation and the capacity operated for each time at the time of the time control operation of a plurality of the compressors 1a are combined in such a manner that pressure fluctuation becomes small. Furthermore, a container such as an oil separator, a liquid receiver, an accumulator, etc., is provided, so that the volume in a high-pressure side or low-pressure side of a refrigerating cycle is a fixed value or more. Also, a circuit that bypasses the low-pressure side and the high-pressure side is provided.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigeration / air-conditioning system using a compressor which is operated at a stepwise operation capacity and switches the capacity step in a short cycle to realize a continuous operation capacity.

[0002]

2. Description of the Related Art A conventional refrigeration / air-conditioning system includes an inverter which continuously adjusts the rotational speed of a compressor and continuously adjusts the operating capacity of a compressor by changing a power supply frequency in accordance with a load. A high-efficiency operation is realized by appropriately controlling the operation capacity of the compressor using this inverter. However, it has been a problem in recent years that harmonics generated by using an inverter get on a power supply and adversely affect other devices. As a countermeasure against harmonics in the case of using an inverter, it can be implemented by using an active filter that prevents harmonics from being output from the refrigeration / air-conditioning apparatus. However, the cost is increased by the amount of the active filter.

Therefore, there have been proposed several methods for continuously adjusting the operating capacity of a compressor by mechanical control without using an inverter. FIG. 34 shows, for example,
FIG. 26 is a refrigerant circuit diagram illustrating an air conditioner provided with a rotary compressor disclosed in Japanese Patent No. 26289. In the figure, 51
Indicates a compressor section of the rotary compressor. The compressor unit 51 has a roller 53 that can rotate eccentrically in a cylinder 52 sandwiched between a main bearing and a sub bearing (neither is shown). A blade 54 is provided in the cylinder 52,
A suction port 55 and a discharge port 56 are arranged on both sides of the blade 54. An indoor heat exchanger 8, an expansion valve 7, and an outdoor heat exchanger 5 are connected via a four-way valve 4 between a suction port 55 and a discharge port 56 of the compressor section 51, and a heat pump type air conditioner is provided. Make up. Reference numeral 57 denotes a refrigerant pipe for connecting the respective components of the refrigeration cycle.

On the other hand, the cylinder 52 of the compressor section 51 includes:
A relief port 58 is provided at a position facing the suction port 55 and the discharge port 56. A valve 59 is provided in the relief port 58, and a pressure switched by the high-pressure side solenoid valve 10 a and the low-pressure side solenoid valve 10 b is introduced from the pressure introduction pipe 60. Reference numeral 61 denotes a spring that applies a biasing force to the valve 59 on the open side.

When the high pressure side solenoid valve 10a is opened and the low pressure side solenoid valve 10b is closed, the valve 59 is pushed down by the discharge pressure to close the relief port 58. When the relief port 58 is closed, the refrigerant being compressed is not bypassed through the relief port 58.
The compressor unit 51 operates at the maximum capacity. Conversely, when the high-pressure side solenoid valve 10a is closed and the low-pressure side solenoid valve 10b is opened, the valve 59 is pushed up by the spring 58 to open the relief port 58. When the relief port 58 is opened, the gas refrigerant being compressed is released from the relief port 5.
8 so that the compressor section 51
The operation capacity at is reduced, and operation at the minimum capacity is implemented.
The opening and closing of the solenoid valves 10a and 10b is controlled by a control circuit (not shown), and the maximum capacity operation and the minimum capacity operation are switched in a short time by a control routine as shown in FIG. The intermediate capacity is variable in multiple stages.

For example, when the control is performed as shown in FIG. 35, the operation is performed at the maximum capacity for 3 seconds and at the minimum capacity for 2 seconds. Therefore, the average operation capacity for 5 seconds is (maximum capacity × 3).
+ Minimum capacity × 2) / 5. By changing the length of the open / close time of the high-pressure side solenoid valve 10a and the low-pressure side solenoid valve 10b, the operation with an intermediate capacity between the maximum capacity and the minimum capacity is continuously realized. According to this method, by adjusting the operation time of the maximum capacity operation and the minimum capacity operation, it is possible to continuously operate at an intermediate capacity between the maximum capacity and the minimum capacity, and the operation capacity control equivalent to that of the inverter becomes possible. . In addition, since an inverter is not used in the operation capacity control of the compressor, electric loss does not occur in the inverter portion, and more efficient operation can be performed.

[0007]

In the conventional refrigeration and air-conditioning system as described above, the operating capacity of the compressor operating at a stepwise capacity is largely switched between the maximum capacity and the minimum capacity, so that pressure fluctuations and the like are reduced. Fluctuations on the refrigeration cycle occur. The maximum operating capacity and the minimum operating capacity required as a compressor are set based on the refrigeration / air-conditioning capacity of the refrigeration / air-conditioning apparatus. For example, refrigeration with a maximum operating capacity of 10 hp (hereinafter, referred to as HP) is performed using a conventional technique. Construct air conditioner, 2HP
In order to realize capacity control continuously up to the operating capacity of the compressor, it is necessary to adopt a configuration in which the maximum operating capacity of the compressor is 10HP and the minimum operating capacity is 2HP. In this case, to achieve an intermediate capacity between the maximum capacity and the minimum capacity,
Since the operation of switching between the maximum operation capacity of 10HP and the minimum capacity of 2HP is performed in a short time, the fluctuation width of the compressor operation capacity is large, and a large pressure pulsation occurs on the refrigeration cycle. With this pressure fluctuation, the amount of heat exchange in the heat exchanger fluctuates greatly in a short time of a few seconds, and when an air heat exchanger is used as the heat exchanger, the fluctuation of the blow-out air temperature increases. However, the refrigerating capacity and the air-conditioning capacity greatly fluctuate in a short time, so that there is a problem that the comfort is impaired.

Further, in order to switch the operating capacity of the compressor in a short time, the number of times of switching between the high pressure side solenoid valve 10a and the low pressure side solenoid valve 10b is increased, and the contact portion in the solenoid valve is opened and closed. There was a problem that a large collision force was applied and the reliability of the solenoid valve drive was reduced, such as a shortened life of the solenoid valve. Further, in this case, since the solenoid valves 10a and 10b are driven in a short time, there is a problem that a driving sound generated when the solenoid valves are opened and closed frequently occurs, and noise occurs.

In addition, since pressure fluctuations occur on the refrigeration cycle, if the operation control of the refrigeration cycle is to be performed by feedback control, the control is performed based on the changed operation information, so that stable control can be performed. There was a problem that there was not.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned conventional problems. In a refrigeration / air-conditioning system equipped with a compressor operable with a stepwise capacity, the adverse effect of harmonics caused by using an inverter is provided. Therefore, the range of fluctuations in the refrigeration cycle, such as pressure fluctuations that occur when the operating capacity of the compressor is switched over in a short cycle to achieve continuous operating capacity, is suppressed. It is an object of the present invention to obtain a refrigeration / air-conditioning apparatus capable of ensuring comfort during driving by reducing fluctuations in performance.

The present invention also relates to a compressor for realizing a continuous operating capacity by switching the operating capacity of a compressor which can be operated with a stepwise capacity in a short cycle, when the operating capacity is switched by a control valve. The aim is to obtain a refrigeration and air-conditioning system that can reduce the driving noise and collision force by frequent opening and closing of the valve, reduce the driving noise and the collision force, realize a low-noise, long-life control valve, and improve the reliability. Is what you do.

Another object of the present invention is to provide a refrigeration / air-conditioning apparatus capable of performing stable operation control by performing control corresponding to the changed operation information.

[0013]

According to a first aspect of the present invention, there is provided a refrigeration / air-conditioning apparatus comprising at least one compressor operable at a stepwise capacity and operating at a stepwise capacity separately from the compressor. At least one compressor capable of operating at a fixed capacity or a compressor operating at a constant capacity is provided. The average capacity in the short cycle is changed by changing the time distribution, so that the total operating capacity of the plurality of compressors is continuously variable.

According to a second aspect of the present invention, in the refrigeration / air-conditioning apparatus according to the first aspect, the operating capacity of the plurality of compressors is shared by at least two compressors that can be operated with a stepwise capacity. When operating the compressor, the operating capacity shared by the compressor operable with the graduated capacity is shared so as not to coincide with the minimum capacity of the graduated capacity of the compressor. Is what you do.

According to a third aspect of the present invention, there is provided a refrigeration / air-conditioning apparatus according to the first or second aspect, wherein at least two compressors operable with stepwise capacities are each allocated with a short cycle time distribution. When operating at different stages of capacity at each of the allocated times, the temporal variation in the short cycle of the total operating capacity of each of the compressors is the larger of the compressors operating in the short cycle. The compressor is operated by combining a short-cycle time distribution of each of the compressors and an operation capacity of each time so as to be smaller than a difference between the total of the operation capacity and the total of the smaller operation capacity. It is.

A refrigeration / air-conditioning apparatus according to claim 4 of the present invention is characterized in that, in claim 3, two compressors operable with a stepwise capacity are provided, and one of the compressors in a short cycle is provided with one of the compressors. At least part of the time during which the larger capacity operation is performed, the other compressor performs the smaller capacity operation of the stage, and the other compressor performs the larger capacity operation of the stage. At least a part of the operation time, one of the compressors is operated at the smaller capacity of the stage.

Further, a refrigeration / air-conditioning apparatus according to claim 5 of the present invention circulates a refrigerant through a compressor, a first heat exchanger, a throttling means, and a second heat exchanger which can be operated in a stepwise capacity. A refrigeration cycle and capacity control means for operating the compressor at different stages of capacity at each time of allocating the short cycle time distribution, and changing the time distribution to change the average capacity in the short cycle. In the refrigeration air conditioner, the internal volume on the high pressure side of the refrigeration cycle is set to a first predetermined volume or more so as to reduce the high pressure side pressure fluctuation range, or the internal volume on the low pressure side of the refrigeration cycle is set to the low pressure side pressure fluctuation. It is characterized in that the width is made equal to or more than a second predetermined volume so as to reduce the width.

The refrigeration and air-conditioning apparatus according to claim 6 of the present invention is characterized in that, in claim 5, the first predetermined volume or the second
The predetermined volume is an allowable value of the pressure fluctuation range on the high pressure side or the low pressure side generated in the refrigeration cycle by operation of the compressor, the length of the short cycle, and the operating capacity fluctuation width of the compressor in the short cycle, It is characterized by having been determined based on.

A refrigeration / air-conditioning apparatus according to a seventh aspect of the present invention circulates a refrigerant through a compressor, a first heat exchanger, a throttling means, and a second heat exchanger that can be operated in a stepwise capacity. A refrigeration cycle, and capacity control means for operating the compressor at different stages of capacity at each time of allocating the short cycle time distribution, and changing the time distribution to change the average capacity in the short cycle. In the refrigeration air conditioner, a refrigerant container is provided on a high pressure side or a low pressure side of the refrigeration cycle, the refrigerant container reducing pressure fluctuation on the high pressure side or the low pressure side generated in the refrigeration cycle by operation of the compressor. It is assumed that.

In the refrigeration / air-conditioning apparatus according to claim 8 of the present invention, the liquid receiver provided at the outlet of a heat exchanger operating as an oil separator or a condenser is used as the refrigerant container provided on the high pressure side. It is characterized by using.

A refrigeration / air-conditioning apparatus according to claim 9 of the present invention is characterized in that, in claim 7, an accumulator provided on a suction side of a compressor is used as a refrigerant container provided on a low pressure side. is there.

A refrigeration / air-conditioning apparatus according to a tenth aspect of the present invention circulates a refrigerant through a compressor, a first heat exchanger, a throttling means, and a second heat exchanger that can be operated with a stepwise capacity. A refrigeration cycle, and capacity control means for operating the compressor at different stages of capacity at each time of allocating the short cycle time distribution, and changing the time distribution to change the average capacity in the short cycle. In the refrigeration air conditioner, a resistance element for adding a flow resistance when a refrigerant flows is provided on a high pressure side or a low pressure side constituting the refrigeration cycle, and a high pressure side or a low pressure generated in the refrigeration cycle by operation of the compressor. It is characterized in that the pressure fluctuation on the side is reduced.

In a refrigeration / air-conditioning apparatus according to claim 11 of the present invention, in claim 10, the resistance element provided on the high pressure side is a check valve provided on the discharge side of the compressor. It is.

A refrigeration / air-conditioning apparatus according to a twelfth aspect of the present invention circulates a refrigerant through a compressor, a first heat exchanger, a throttling means, and a second heat exchanger which can be operated in a stepwise capacity. A refrigeration cycle and capacity control means for operating the compressor at different stages of capacity at each time of allocating the short cycle time distribution, and changing the time distribution to change the average capacity in the short cycle. In the refrigeration air conditioner, a bypass circuit that bypasses a high pressure side and a low pressure side of the refrigeration cycle is provided, and a pressure fluctuation on a high pressure side or a low pressure side generated in the refrigeration cycle by operation of the compressor is reduced. Is what you do.

According to a thirteenth aspect of the present invention, in the refrigeration / air-conditioning apparatus according to the twelfth aspect, the bypass circuit is a circuit connecting the discharge side and the suction side of the compressor. .

According to a fourteenth aspect of the present invention, there is provided a refrigeration / air-conditioning apparatus according to the twelfth or thirteenth aspect, wherein a control valve is provided in the bypass circuit, and the compressor operable in a stepwise capacity is provided with a short cycle compressor. When operating at different stages of capacity at each time of the time distribution, the control valve opens the bypass circuit, and when the compressor operates at a constant capacity, the control valve closes the bypass circuit. It is characterized by doing.

In the refrigeration / air-conditioning apparatus according to claim 15 of the present invention, in claim 12, the bypass circuit is configured to supply the high-pressure liquid refrigerant condensed by the heat exchanger operating as a condenser of the refrigeration cycle to the compressor suction side. It is characterized by being a circuit for returning to.

The refrigeration / air-conditioning apparatus according to claim 16 of the present invention is characterized in that,
A pressure reducing means for reducing the pressure of the high-pressure liquid refrigerant is provided, and a heat exchanger for exchanging heat between the refrigerant decompressed by the pressure reducing means and the high-pressure liquid refrigerant condensed by the condenser is provided.

A refrigeration / air-conditioning apparatus according to claim 17 of the present invention is characterized in that, in claim 12, the bypass circuit is a circuit for returning the oil separated by the oil separator to the low pressure side.

In the refrigeration / air-conditioning apparatus according to the eighteenth aspect of the present invention, the refrigerant is circulated through the compressor, the first heat exchanger, the throttling means, and the second heat exchanger which can be operated in a stepwise capacity. A refrigeration cycle, capacity control means for operating the compressor at different stages of capacity at each time of allocating the short cycle time distribution, and changing the time distribution to change the average capacity in the short cycle; and In a refrigeration / air-conditioning apparatus provided with a control valve for switching the operating capacity of the compressor in the short cycle time distribution, oil supply means for supplying oil to the control valve is provided.

In the refrigeration / air-conditioning apparatus according to claim 19 of the present invention, an oil separator is provided on the discharge side of the compressor, and the oil supply means includes oil separated by the oil separator or oil separation oil. It is an oil supply circuit for supplying the refrigerant gas after the cooling to the control valve.

[0032] In the refrigeration / air-conditioning apparatus according to claim 20 of the present invention, in claim 18, the oil supply means is an oil supply circuit for supplying gas refrigerant discharged from the compressor to a control valve. It is assumed that.

A refrigeration / air-conditioning apparatus according to a twenty-first aspect of the present invention circulates a refrigerant through a compressor, a first heat exchanger, a throttling means, and a second heat exchanger that can be operated in a stepwise capacity. A refrigeration cycle, capacity control means for operating the compressor at different stages of capacity at each time of allocating the short cycle time distribution, and changing the time distribution to change the average capacity in the short cycle; and In a refrigeration / air-conditioning apparatus provided with a control valve for switching the operating capacity of the compressor in the short cycle time distribution, a cooling means for cooling the control valve is provided.

In the refrigeration / air-conditioning apparatus according to claim 22 of the present invention, in claim 21, the cooling means supplies the control valve with the high-pressure liquid refrigerant condensed by the heat exchanger operating as a condenser of the refrigeration cycle. It is characterized by being a refrigerant circuit.

A refrigeration / air-conditioning apparatus according to a twenty-third aspect of the present invention is the refrigeration / air-conditioning apparatus according to the twenty-first aspect, wherein the cooling means is configured to cool the control valve by outside air around the refrigeration / air-conditioning apparatus. is there.

A refrigeration / air-conditioning apparatus according to a twenty-fourth aspect of the present invention circulates a refrigerant through a compressor, a first heat exchanger, a throttling means, and a second heat exchanger that can be operated in a stepwise capacity. A refrigeration cycle, capacity control means for operating the compressor at different stages of capacity at each time of allocating the short cycle time distribution, and changing the time distribution to change the average capacity in the short cycle; In a refrigeration / air-conditioning apparatus including a control valve that switches the operating capacity of the compressor in the short-period time distribution by opening and closing a flow path by moving a valve, a portion that comes into contact with the control valve by moving the movable valve. Alternatively, the movable valve corresponding to the contact portion is provided with an impact mitigation means for alleviating the impact.

According to a refrigeration / air-conditioning apparatus according to claim 25 of the present invention, in claim 24, the shock absorbing means is provided by at least a portion of a portion of the movable valve which contacts the moving valve or a material of the movable valve which contacts the contact portion. Is made of resin to mitigate the impact.

In the refrigeration / air-conditioning apparatus according to claim 26 of the present invention, in claim 24, the shock absorbing means is provided with a deceleration means for decelerating the movement of the movable valve. The speed is reduced to reduce the impact.

A refrigeration / air-conditioning apparatus according to a twenty-seventh aspect of the present invention circulates a refrigerant through a compressor, a first heat exchanger, a throttling means, and a second heat exchanger which can be operated with a stepwise capacity. A refrigeration cycle, capacity control means for operating the compressor at different stages of capacity at each time when the short cycle time distribution is distributed, and changing the time distribution to change the average capacity in the short cycle, Measuring means for measuring the operation information of the refrigeration cycle in a plurality of times within a predetermined time longer than the short cycle, based on the obtained plurality of operation information, the capacity control means, The refrigeration cycle control including the control is performed.

A refrigeration / air-conditioning apparatus according to claim 28 of the present invention is configured by circulating a refrigerant through a compressor, a first heat exchanger, a throttling means, and a second heat exchanger operable in a stepwise capacity. A refrigeration cycle, capacity control means for operating the compressor with different capacities at different times to which the short cycle time distribution is allocated, and changing the time distribution to change the average capacity in the short cycle; Measuring means for measuring the operation information of the refrigeration cycle at a predetermined time within the short cycle, based on the obtained operation information, control of the refrigeration cycle including control by the capacity control means It is characterized by performing.

A refrigeration / air-conditioning apparatus according to claim 29 of the present invention is characterized in that, in any one of claims 5 to 28, the refrigeration cycle can be operated with a stepwise capacity separately from the compressor. It is characterized by comprising at least one compressor or a compressor operating at a fixed capacity.

[0042]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiment 1 Hereinafter, as a refrigeration / air-conditioning apparatus according to Embodiment 1 of the present invention, for example, an apparatus for performing indoor air conditioning will be described. FIG. 1 is a refrigerant circuit diagram showing a configuration of a refrigeration / air-conditioning apparatus according to the present embodiment. In the figure, reference numeral 1a denotes a compressor which can be operated with a stepwise capacity, for example, a scroll compressor provided with bypass capacity control means,
b is a compressor of a fixed capacity, 2a and 2b are discharge pipes, 3a,
3b is a suction pipe, 4 is a refrigerant flow switching means for cooling operation and heating operation, for example, a four-way valve, 5 is a first heat exchanger, for example, an outdoor heat exchanger, 6 is a liquid pipe, 7a and 7b are throttle means. For example, expansion valves, 8a and 8b are second heat exchangers, for example, indoor heat exchangers, and 9 is a gas pipe. A refrigeration cycle is configured by connecting these devices and pipes to circulate the refrigerant.

10a and 10b are scroll compressors 1
a control valve for controlling the operating capacity of a, 10a is a high-pressure side solenoid valve provided, for example, on a pipe 11a from a discharge pipe 2a, and 10b is a low-pressure side solenoid valve provided on a pipe 12a, for example, from a suction pipe 3a It is. Solenoid valves 10a, 10b
Are connected to each other and connected to the scroll compressor 1a via a capacity control piping 15a of the scroll compressor 1a. Further, the maximum operating capacity of the refrigeration air conditioner in the present embodiment is 10 HP, and
Is a compressor capable of switching the capacity stepwise between a maximum capacity of 6HP and a minimum capacity of 2HP, and the compressor 1b is a compressor operating at a constant capacity of 4HP. That is, two compressors are provided, a compressor 1a having a maximum capacity of 6HP and a compressor 1b having a maximum capacity of 4HP.
Thus, a refrigeration air conditioner having a maximum capacity of 10 HP is configured. Here, for example, a cooling capacity of about 2.8 kW can be supplied with an operating capacity of 1 HP.

Next, the flow of the refrigerant in the refrigeration cycle of this embodiment will be described. In the cooling operation, the four-way valve 4 is set so as to flow in the direction of the solid line in FIG. The high-temperature and high-pressure gas refrigerant discharged from the compressors 1a and 1b is condensed and liquefied in the outdoor heat exchanger 5 through the discharge pipes 2a and 2b and the four-way valve 4, and then decompressed by the expansion valves 7a and 7b through the liquid pipe 6. Then, it becomes a low-pressure two-phase refrigerant and flows into the indoor heat exchangers 8a and 8b. Further, the low-pressure two-phase refrigerant is supplied to the indoor heat exchanger 8a,
In step 8b, the inside of the room is deprived of heat while evaporating and gasifying to cool the room. Thereafter, the refrigerant flows through the gas pipe 9, the four-way valve 4, and the suction pipes 3a and 3b, and is sucked into the compressors 1a and 1b. On the other hand, in the heating operation, the flow path is set so that the four-way valve 4 flows in the direction of the broken line in FIG. The high-temperature and high-pressure gas refrigerant discharged from the compressors 1a and 1b is discharged from the discharge pipes 2a and 2b.
b, the indoor heat exchangers 8a and 8b via the four-way valve 4 and the gas pipe 9.
While being condensed and liquefied by flowing into the room, heat is supplied to the room side to heat the room. Thereafter, the pressure is reduced by the expansion valves 7a and 7b to become a low-pressure two-phase refrigerant. The refrigerant is vaporized and gasified by the outdoor heat exchanger 5 through the liquid pipe 6, and then the four-way valve 4, the suction pipes 3a and 3
b, and is sucked into the compressors 1a and 1b.

Next, the capacity control operation of the compressor 1a will be described. Here, the compressor 1a is a scroll compressor that can be operated in two stages of a maximum capacity (6HP) and a minimum capacity (2HP). The side solenoid valve 10b is closed. As a result, the capacity control pipe 15 communicates with the discharge pipe 2a,
A high pressure state results. Conversely, when operating the compressor 1a with the minimum capacity, the high pressure side solenoid valve 10a is closed and the low pressure side solenoid valve 10a is closed.
Open b. As a result, the capacity control pipe 15 becomes the suction pipe 3
a and a low pressure state is established.

The operation of the scroll compressor at this time is shown in FIG.
And FIG. FIG. 2 is a sectional view showing a compression chamber of the scroll compressor 1a, and FIG. 3 is a plan view as seen from a section AA in FIG. In the drawing, reference numeral 20 denotes a fixed scroll, in which a spiral 20b is provided on the lower surface of the base plate portion 20a, and a discharge port 20c is opened. Reference numeral 21 denotes an orbiting scroll, and a spiral 21b is combined with an upper surface of a base plate portion 21a to form a compression chamber 22. An orbiting shaft 21c formed below the base plate of the orbiting scroll is connected to a bearing eccentric to a rotating shaft (not shown) connected to an electric motor (not shown), and a rotation preventing member (not shown). As a result, a so-called swinging motion of revolving while being prevented from rotating is performed. For this reason, the compression chamber 2
2 is formed by the fixed-side spiral 20b and the swing-side spiral 21b. Outside the compression chamber 22, that is, the spiral 20
As the low-pressure gas refrigerant flows in from the outer periphery of b and 21b and is conveyed to the center side, the volume is reduced and the pressure is increased, and is sent out from the discharge port 20c to the discharge pipe 27 as a high-temperature and high-pressure gas refrigerant. .

The following mechanism is provided on the base plate portion 20a of the fixed scroll 20 as a capacity control means. 23
a is a pair of bypass holes provided in the compression chamber 22 from the outside of the spiral so as to be symmetrical with respect to the center portion;
It communicates with a large-diameter valve seat hole 23b provided above.
An annular slit 23c concentric with the hole is provided in the bypass hole 23a, and a discharge port 23d is opened from the annular slit 23c to the outside low-pressure portion. 24 is the valve seat hole 2
The control valve is in contact with the valve seat at the bottom of 3b and closes the bypass hole 23a, and is pressed upward by a compression spring 25 inserted into the annular slit 23c. 26 is the valve seat hole 2
A communication hole 26a is opened by a valve seat plug attached to the upper part of 3b, and a pressure pipe 23 connected to the capacity control pipe 15a is connected.

When high-pressure refrigerant is added to the pressure pipe 23 from the capacity control pipe 15a through the discharge pipe 2a and the low-pressure refrigerant from the suction pipe 3a is cut off, the control valve 24 is pressed downward and the bypass hole 23a is pressed. Is closed, the entire amount of the refrigerant gas in the compression chamber 22 is compressed and sent out from the discharge port 20c without being bypassed, and the compressor 1a operates at the maximum capacity.

Next, the capacity control pipe 1 is connected to the pressure pipe 23.
From 5a, low-pressure refrigerant is added through the suction pipe 3a,
When the high-pressure refrigerant from the discharge pipe 2a is cut off, the compression chamber 22
The control valve 24 is pushed up by the pressure and the compression spring 25 to come into contact with the valve seat plug 26 to close the communication hole 26a. Thereby, the bypass hole 23a and the discharge hole 23d communicate with each other, and a part of the refrigerant gas in the compression chamber 22 is discharged to the low-pressure part in the compressor,
The compressor 1a operates at the minimum capacity due to the decrease in the amount of refrigerant sent from the discharge port 20c.

When the compressor 1a operable with two stages of capacity, the maximum capacity and the minimum capacity, is operated with the capacity between the two stages, the maximum capacity operation and the minimum capacity operation are distributed in a short period of time. It is realized by switching with. Further, the time distribution of the short cycle of the maximum capacity operation and the minimum capacity operation is changed to change the average capacity in the short cycle, and the compressors 1a, 1b
Can be continuously changed.

Hereinafter, a method for controlling the operating capacity of the compressors 1a and 1b will be described. The required operating capacity of the compressors 1a and 1b in total is the operating state of the refrigerating air conditioner, the outside air temperature, the indoor air temperature, the target value of the indoor air temperature, the indoor heat exchanger 8
a, 8b and the like. For example,
When the required operating capacity of the compressors 1a and 1b is determined based on the operating state of the refrigeration and air conditioning system, the operating capacity is determined as follows. During the cooling operation, the low pressure side of the refrigeration cycle, for example, the pressure on the compressor suction side is measured, and the measured low pressure value is compared with a predetermined low pressure target value. As a result of this comparison, if the measured value is higher than the target value, the operating capacity is made larger than the current compressor operating capacity, and if the measured value is lower than the target value, the operating capacity is made larger than the current compressor operating capacity. Make it smaller. During the heating operation, the high-pressure side pressure of the refrigeration cycle, for example, the pressure on the compressor discharge side is measured, and the measured high-pressure value is compared with a predetermined high-pressure target value. If the measured value is higher than the target value, The operating capacity is made smaller than the current compressor operating capacity. Conversely, if the measured value is lower than the target value, the operating capacity is made larger than the current compressor operating capacity.

The required operating capacity of the compressors 1a and 1b is
When determining from the indoor air temperature and the indoor air temperature target value set by the user of the refrigeration / air-conditioning system using a remote controller or the like, the operating capacity is determined as follows. During the cooling operation, the indoor air temperature is measured, and the measured value is compared with the indoor air temperature target value. As a result of this comparison, if the measured value is higher than the target value, the operating capacity is made larger than the current compressor operating capacity, and if the measured value is lower than the target value, the operating capacity is made larger than the current compressor operating capacity. Make it smaller. Similarly, during the heating operation, the indoor air temperature is measured, and the measured value is compared with the indoor air temperature target value. ,
Conversely, if the measured value is lower than the target value, the operating capacity is made larger than the current compressor operating capacity.

When the required operating capacity of the compressor is determined from the operating capacity of the indoor heat exchangers 8a and 8b, if the operating capacity of the indoor heat exchangers 8a and 8b is large, the compressor is required as a refrigerating air conditioner. Since the load increases, the operating capacity of the compressor is increased. Conversely, if the operating capacity of the indoor heat exchangers 8a and 8b is small, the load required as a refrigeration / air-conditioning device is reduced, so that the operating capacity of the compressor is reduced.

The outside air temperature affects the load of the refrigeration and air conditioning system. If the outside air temperature is low, the cooling load decreases and the heating load increases, so that the operating capacity of the compressor is adjusted to be small during the cooling operation. In the heating operation, the necessary operating capacity of the compressor is adjusted by, for example, adjusting the operating capacity of the compressor to a large value.

According to the required operating capacity of the compressor determined as described above, the high-pressure solenoid valve 10a and the low-pressure solenoid valve 10b of the compressor 1a are opened and closed in a short cycle, and the fixed-capacity compressor 1b is opened. Implement capacity control by combining operation and stop. Table 1 shows that the high pressure side solenoid valve 10a and the low pressure side solenoid valve 1
0b and the operation and stoppage of the fixed capacity compressor 1b. In the capacity control of the compressor 1a, for example, 1
The maximum capacity operation (6HP) when the high-pressure solenoid valve 10a is opened (the low-pressure solenoid valve 10b is closed) and when the low-pressure solenoid valve 10b is opened (the high-pressure solenoid valve 10a is closed), with 0 second as one cycle. Time distribution with a short cycle of 10 seconds is distributed in two stages of the minimum capacity operation (2HP).

[0056]

[Table 1]

For example, when the total operating capacity in Table 1 is 3HP, the compressor 1a has a short cycle time distribution of 2.5 seconds for the maximum capacity operation of 6HP and 7.5 for the minimum capacity operation of 2HP.
Assuming seconds, the short-cycle average capacity is (6 × 2.5 + 2 ×
7.5) / 10 = 3, and the compressor 1b is stopped, so that 3HP is obtained as the total operating capacity. Also,
When the total operating capacity is 9HP, the compressor 1a performs the maximum capacity operation of 6HP for 7.5 seconds and 2H as a short cycle time distribution.
Assuming that the minimum capacity operation of P is 2.5 seconds, the short-cycle average capacity is (6 × 7.5 + 2 × 2.5) / 10 = 5,
Since the compressor 1b (operating capacity of 4HP) is operating,
9HP is obtained as the total operating capacity. in this way,
The time distribution of the short cycle of the maximum capacity operation and the minimum capacity operation is changed to change the average capacity in the short cycle, and the compressors 1a, 1
The total operating capacity of b can be changed continuously and arbitrarily. Here, an operation in which the capacity is changed stepwise in a short period with a predetermined time distribution is referred to as a time control operation.

In the operation of the high-pressure side solenoid valve 10a and the low-pressure side solenoid valve 10b in Table 1, as shown in FIG. 4, the opening and closing are controlled so that one of them is always opened and one of them is closed. FIG. 5 shows changes in the operating capacity of the compressors 1a and 1b, and shows the compressor operating capacity [H] with respect to the required operating capacity [HP].
P] is a graph showing the change in the total operating capacity of the compressor realized by Table 1. By operating with the compressor capacity as shown in Table 1, in the present embodiment, the total operating capacity of the plurality of compressors 1a and 1b is 2HP to 1HP.
The operating capacity can be continuously changed up to 0HP.

Looking at the fluctuation width of the operating capacity in a short cycle in this case, when the operating capacity is 6 HP to 10 HP, the compressor 1 a
Is operated at a total capacity of 10 HP when the compressor 1a is operated at the maximum capacity, and is operated at a total capacity of 6 HP when the compressor 1a is operated at the minimum capacity. I will drive. That is, the operating capacity is 1 in a short cycle.
It fluctuates between 0HP and 6HP. Therefore, even if the air conditioner realizes a continuous operation capacity from 2 HP to 10 HP, the operation capacity fluctuates between 10 HP and 2 HP in a short cycle when operating with one compressor as in the related art. On the other hand,
In the present embodiment, the fluctuation width of the operating capacity can be reduced. If the fluctuation width of the operating capacity can be reduced, the pressure pulsation generated on the refrigeration cycle will be reduced, and the fluctuation width of the heat exchange amount in the heat exchanger, and the blowout air temperature when the air heat exchanger is used as the heat exchanger The fluctuation of the refrigeration capacity and the air conditioning capacity of the refrigeration / air-conditioning apparatus, such as the fluctuation width of the refrigeration / air-conditioning apparatus, can be reduced, and the comfort during the operation of the refrigeration / air-conditioning apparatus can be secured.

When the operating capacity is 2HP to 6HP, the operating capacity fluctuates between 2HP and 6HP in a short period. In this case as well, when operating with one compressor as in the prior art, the operating capacity fluctuates between 10HP and 2HP in a short time, whereas in the present embodiment, the fluctuation range of the operating capacity can be reduced. Also in this case, the fluctuation width of the operating capacity can be reduced, the fluctuation width of the pressure pulsation generated on the refrigeration cycle, the fluctuation width of the heat exchange amount in the heat exchanger, and the outlet air temperature when the air heat exchanger is used as the heat exchanger Can be reduced, and fluctuations in the refrigeration capacity and the air conditioning capacity of the refrigeration / air-conditioning apparatus can be reduced, so that comfort during operation of the refrigeration / air-conditioning apparatus can be ensured.

As described above, in the present embodiment, the compressor 1a that can be operated with a stepwise capacity and the compressor 1b that can be operated with a fixed capacity are provided, and the inverter is operated without using the inverter, so that the inverter can be operated. There is no adverse effect of higher harmonics due to the use of the compressor, and the operating capacity of the compressor 1a is switched in a short cycle to realize a continuous operating capacity, thereby reducing the capacity fluctuation width, and thereby causing refrigeration such as pressure fluctuations caused by this. The fluctuation width on the cycle can be suppressed. For this reason, fluctuations in the refrigeration capacity and air conditioning capacity such as fluctuations in the temperature of the blown air can be reduced, and a refrigeration / air-conditioning apparatus can be obtained that can ensure comfort during operation.

In Table 1, the switching cycle of the operating capacity is performed at intervals of 10 seconds (the total time of the operating time of the maximum capacity and the operating time of the minimum capacity). It is determined by the fluctuation width of the blown air temperature when an air heat exchanger is used as the exchanger. For example, when the air heat exchanger is used as the heat exchanger in order to ensure the comfort during the operation of the refrigeration air conditioner, the fluctuation range of the blown air temperature is 1 ° C.
When you Osaeyo the extent, pressure fluctuation range of the refrigeration cycle is 2 kgf / cm ² at high pressure, it is necessary to set the following order of 1 kgf / cm ² at low pressure. The switching interval of the operation capacity to suppress the pressure fluctuation width varies depending on the stepwise operation capacity fluctuation width within the short period, that is, the difference between the maximum capacity and the minimum capacity, but in a general refrigeration cycle, it is approximately several seconds. The interval is set to several tens of seconds.

In the above description, the compressor 1a is a compressor that can be operated with two stages of capacity, a maximum capacity and a minimum capacity. However, the compressor is not limited to two stages and can be operated with more stages. If a compressor is used, the operation pattern increases and the operation control becomes complicated, but the difference in the operation capacity that is switched by short-cycle time distribution can be reduced, and the pressure fluctuation of the refrigeration cycle can be further reduced. Comfort is increased. In the scroll compressor shown in FIGS. 2 and 3,
In order to obtain two or more stages of operating capacity, for example, the compression chamber 22 outside the bypass hole 23a that realizes the minimum capacity is used.
This can be realized by providing another bypass hole communicating with the low-pressure pipe, and closing and opening this hole to change the amount of refrigerant gas in the compression chamber 22.

In the above description, a combination of one compressor operable with a stepwise capacity and one compressor having a constant capacity has been described. When a plurality of compressors are combined, a plurality of compressors that can be operated with a stepped capacity and one compressor with a fixed capacity are combined, and when a plurality of compressors that can be operated with a stepped capacity are combined with a fixed capacity, When a plurality of compressors are combined, the same effect can be obtained in any case.
In addition, in view of the effect that the pressure fluctuation of the refrigeration cycle can be reduced, providing a large number of capacity stages of the compressor that can be operated with stepwise capacity reduces the capacity difference that is switched in a short cycle than a small number of capacity stages. Effective because it can. In addition, the larger the number of compressors, the smaller the switching capacity in a shorter cycle than the smaller number of compressors.
It is effective.

Embodiment 2 Hereinafter, as a refrigeration / air-conditioning apparatus according to Embodiment 2 of the present invention, for example, an apparatus for performing indoor air-conditioning will be described. FIG. 6 is a refrigerant circuit diagram showing a configuration of the refrigeration / air-conditioning apparatus according to the present embodiment. In the figure, 1
c is a compressor which can be operated with a stepwise capacity, for example, a scroll compressor provided with bypass capacity control means, 10c, 1c
0d is a control valve for controlling the operating capacity of the scroll compressor 1c, and 10c is, for example, a pipe 1 from the discharge pipe 2b.
The high-pressure side solenoid valve provided in 1b is a low-pressure side solenoid valve provided in the pipe 12b from the suction pipe 3b, for example. The pipes 13b and 14b from the solenoid valves 10c and 10d are connected to each other to control the capacity of the scroll compressor 1c.
5b is connected to the scroll compressor 1c.
The maximum operating capacity of the refrigeration and air-conditioning system according to the present embodiment is 1
0HP, the compressor 1a is a compressor capable of stepwise capacity switching between a maximum capacity 6HP and a minimum capacity 4HP, and the compressor 1c is a compressor capable of stepwise capacity switching between a maximum capacity 4HP and a minimum capacity 2HP. is there. That is, two compressors which can be operated in stepwise capacities are provided, and the compressor 1a having a maximum capacity of 6HP and the compressor 1c having a maximum capacity of 4HP have a maximum capacity of 10HP.
The refrigeration air conditioner of the HP is configured. The other elements in FIG. 6, the flow of the refrigerant, and the method of switching the capacity of the compressor in FIG. 6 are the same as those in the first embodiment, and thus description thereof will be omitted.

In the present embodiment, in the same manner as in the first embodiment, the required operating capacity of the compressor is determined by the operating state of the refrigerating air conditioner, the outside air temperature, the indoor air temperature, the target value of the indoor air temperature,
It is determined by the operating capacity of the indoor heat exchangers 8a and 8b and the like. Then, according to the determined required operating capacity of the compressor, the high-pressure side solenoid valves 10a and 10c and the low-pressure side solenoid valves 10b and 10d of the compressors 1a and 1c are opened and closed in a short cycle, and the compressors 1a and 1c are opened and closed. Implement capacity control by combining operation and stop. Table 2 shows that the high pressure side solenoid valve 10a and the low pressure side solenoid valve 10b of the compressor 1a are opened / closed, operated, and stopped when obtaining the total operation capacity of 2HP to 10HP, and the high pressure side solenoid valve 10c and the low pressure side solenoid of the compressor 1c. Opening and closing of valve 10d, operation,
Indicates a stop. Also in the capacity control of each of the compressors 1a and 1c, for example, 10 seconds is set to 1 as in the first embodiment.
Maximum capacity operation when the high-pressure side solenoid valves 10a and 10c are opened (the low-pressure side solenoid valves 10b and 10d are closed).
HP, 4HP) and the minimum capacity operation (4HP, 2HP) when the low-pressure side solenoid valves 10b, 10d are opened (the high-pressure side solenoid valves 10a, 10c are closed). I'm sorting. By changing this time distribution to change the average capacity in a short cycle, the compressor 1
The sum of the operating capacities a and 1c can be continuously and arbitrarily changed.

[0067]

[Table 2]

The high pressure side solenoid valves 10a, 10c in Table 2
In operation of the low-pressure side solenoid valves 10b and 10d, as shown in FIG. 4, opening and closing are controlled so that one of them is always opened and one of them is closed. FIG. 7 is a graph showing a change in the operating capacity of the compressors 1a and 1c and showing the compressor operating capacity [HP] with respect to the required operating capacity [HP]. It is a diagram illustrating the change.

Looking at the fluctuation width of the operating capacity in this case in a short time, when the operating capacity is 8 HP to 10 HP, the compressor 1 a
Is operated at a total capacity of 10 HP when the compressor 1a is operating at the maximum capacity, and is operated at a total capacity of 8 HP when the compressor 1a is operating at the minimum capacity. I will drive. That is, the operating capacity is 1 in a short cycle.
It fluctuates between 0HP and 8HP. At other operating capacities,
When the operating capacity is 6HP to 8HP, the operating capacity fluctuates between 8HP and 6HP in a short time. When the operating capacity is 4HP to 6HP, the operating capacity fluctuates between 4HP and 6HP in a short time, and the operating capacity is 2HP to 4HP. , The operating capacity fluctuates between 2HP and 4HP in a short time. Therefore, a plurality of compressors 1
The operating capacity can be continuously realized from 2HP to 10HP as a whole of a and 1c. In this case, when the inverter is not used and the compressor is operated by one compressor as in the related art, the operating capacity is determined. Fluctuates between 10HP and 2HP in a short cycle, but the fluctuation width of the operating capacity can be reduced. Further, it is possible to perform an operation in which the fluctuation range of the operation capacity is smaller than in the first embodiment.

As described above, in the present embodiment, the two compressors 1a and 1c which can be operated with stepwise capacities are provided, and the operation is performed without using the inverter. No adverse effect of the compressor 1
When the operating capacities a and 1c are switched in a short cycle to realize a continuous operating capacity, the fluctuation width of the capacity can be reduced, and the fluctuation width on the refrigeration cycle such as the pressure fluctuation caused by this can be suppressed. For this reason, fluctuations in the refrigeration capacity and air conditioning capacity such as fluctuations in the temperature of the blown air can be reduced, and a refrigeration / air-conditioning apparatus can be obtained that can ensure comfort during operation.

Here, the combination in which the operating capacity is continuously changed between 2HP and 10HP by the two compressors 1a and 1c which can be operated with the stepwise capacity is not limited to the method shown in Table 2 and FIG. . In the control in Table 2, as can be seen from FIG. 7, in the operating capacity range of 6HP to 10HP, the time control operation of the compressor 1a is performed at 8HP to 10HP, and the compressor 1c is controlled at 6HP to 8HP. Although the time control operation is performed, as shown in FIG.
The time control operation of the compressor 1c may be performed in the range of 10HP, and the time control operation of the compressor 1a may be performed in the range of 6HP to 8HP.

Also, as shown in FIG.
A capacity control method in which the compressors 1a and 1c perform time control operation in the range of P may be performed. Table 3 shows the capacity control of the compressors 1a and 1c at this time. When a plurality of compressors that can be operated at a plurality of stepwise capacities are provided, each compressor is controlled so as not to operate at the minimum capacity of that step during a short period. Therefore, if the operating capacity is larger than the sum of the smaller capacities of the compressors 1a and 1b (6HP) and smaller than the sum of the larger capacities (10HP), the two compressors 1
The time control operation is performed in both a and 1c. When the total operating capacity is 4HP, there are two types of operation: the compressor 1a operates at the minimum capacity and the compressor 1b operates at the maximum capacity. However, the minimum capacity operation at the compressor 1a is avoided and the compressor 1b is operated. Perform maximum capacity operation at.

[0073]

[Table 3]

In the compressor provided with the bypass displacement control means, when performing the minimum displacement operation, the influence of the bypass causes
The discharge temperature of the compressor increases as compared with the case where the maximum displacement operation is performed. Therefore, as shown in FIGS.
Minimum capacity operation with one compressor 1a as in the case of HP,
In the case of another one compressor 1c having the maximum capacity operation,
The discharge temperature of the compressor 1a operating at the minimum capacity is higher than that of the compressor 1c operating at the maximum capacity. In this case, the discharge temperature is detected as the operation protection of the compressor, and when the discharge temperature rises to a certain temperature or higher, the compressor is stopped. Occurs, and stable operation cannot be performed.
Therefore, as shown in FIG.
By performing time control operation on both compressors 1a and 1b in the range from
When the operation protection of the compressor is executed by detecting the discharge temperature,
In the case of an operating condition requiring operation protection, both compressors can be stopped at the same time. Otherwise, the operation of both compressors can be continued, so that stable operation can be performed. However, this does not apply to the case where an operating capacity value cannot be obtained unless a certain compressor is operated at the minimum capacity among a plurality of stages, for example, when the total operating capacity in Table 3 is 2HP.

As described above, in the case of a refrigeration / air-conditioning system having a plurality of compressors which can be operated with stepwise capacity, the operating capacity of the plurality of compressors is shared by the compressors which can be operated with stepwise capacity. When operating the compressor, it is possible to make the discharge temperature of the operating compressor equal by avoiding that the operating capacity shared by the compressor coincides with the minimum capacity of the stepwise capacity of the compressor. In addition, it is possible to prevent the discharge temperature of a specific compressor from increasing. The operating capacity 0HP can be used as the operating capacity of the compressor 1a that can be operated at a stepwise capacity. However, at 0HP, the operation is not performed, so that the discharge temperature does not increase. Does not happen. Therefore, it is not considered as the minimum capacity here. That is, the minimum capacity is the minimum capacity among the stepwise capacities larger than 0HP. In addition to operating the compressor so as to avoid the minimum capacity of the compressor that can be operated with stepwise capacity as much as possible, when realizing a certain operating capacity, there are a plurality of combinations in which a plurality of compressors share the operating capacity. At this time, it is preferable to select a combination that can reduce the variation in the discharge temperature of the operating compressor from among those combinations. When operating with an operating capacity that is greater than the sum of the minimum capacities of the respective compressor capacity stages and smaller than the sum of the maximum capacities, a time-controlled operation of a plurality of compressors is required. It is possible to prevent the temperature of the refrigerant discharged from the compressor from rising, and to perform a stable operation.

FIG. 10 and FIG. 11 are explanatory diagrams showing the change over time of the operating capacity of each compressor according to the present embodiment.
The horizontal direction indicates time, and the vertical direction indicates compressor operating capacity.
In the time control operation when the operation capacity control as shown in FIG. 9 is performed, as shown in FIG. 10, when the operation with the large capacity and the operation with the small capacity of the compressors 1a and 1c are operated at the same timing, the operation becomes The capacity is short-cycle (large capacity of compressor 1a + large capacity of compressor 1c = 10HP) and (compressor 1
(a small capacity of a + a small capacity of the compressor 1c = 6HP). On the other hand, as shown in FIG.
When the operation with the large capacity a and 1c and the operation with the small capacity are operated at opposite timings (opposite phases), the fluctuation of the operation capacity in a short cycle is (large capacity of the compressor 1a + small capacity of the compressor 1c). (Capacity = 8HP) and (small capacity of the compressor 1a + large capacity of the compressor 1c = 8HP), so that the operation can be performed with almost no change in capacity as a whole.
Therefore, when the compressors 1a and 1c perform the time control operation by performing the capacity control, the compressors 1a and 1c
By operating such that the operation with the large capacity and the small capacity of the compressor is operated at the opposite timing (opposite phase), the fluctuation width of the total operating capacity of the compressors 1a and 1c can be reduced. Therefore, comfort during operation of the refrigeration / air-conditioning apparatus can be ensured.

In the above description, the time control operation is performed by two compressors. The operation of the stepwise capacity is performed at the opposite timing. However, when the time control operation is performed by three or more compressors, It is difficult to set a stepwise capacity operation at the opposite timing. In this case, it is preferable to combine the changes in the short-period capacity operation of each compressor so that the temporal fluctuation of the total operating capacity of each compressor within the short cycle is reduced. For example, in a short cycle, the compressor A
P, compressor B is 4HP and 2HP, compressor C is 3HP and 2HP
When the capacity change operation of the HP is performed, when the operation is performed with a capacity of 4 HP in the compressor A, 2 HP in the compressor B, and 3 HP in the compressor C, the total of the operation capacity becomes 9 HP, and the time distribution is performed. On the other hand, compressor A is 2HP, compressor B
When the compressor is operated with a capacity of 4HP and the compressor C with a capacity of 2HP, the total operating capacity becomes 8HP, and the capacity fluctuation in a short cycle is 9H.
It can be operated to keep P-8HP = 1HP as small as possible. Of course, the time distribution is different between the compressors, and as in the case of two compressors, if the operation is performed at this timing so as to be as long as possible, the fluctuation in capacity can be minimized.

Of course, it is preferable to minimize the temporal fluctuation of the total operating capacity of each compressor within a short cycle as in the above specific example, since the pressure fluctuation is reduced. Instead, it is preferable to combine the compressors so that the total temporal fluctuation of the operating capacity of each compressor is slightly reduced. That is, when a plurality of compressors are operated in a time-controlled manner, the combination having the largest temporal variation in the total operating capacity of each compressor in the short cycle is larger in all the compressors in the short cycle. This is when the operation is performed with the smaller capacity and all the compressors are simultaneously switched to the smaller capacity.
At this time, the change in capacity in a short cycle is the difference between the sum of the larger capacity and the sum of the smaller capacity. Therefore, in the present embodiment, the temporal variation in the short cycle of the total operating capacity of each compressor is different from the total of the larger operating capacity and the smaller operating capacity of each compressor operating in the short cycle. The compressor is operated by combining the short-cycle time distribution of each compressor and the operation capacity at each time so that the difference between the compressor and the total capacity is smaller than the difference. By operating in this manner, the temporal fluctuation width of the operating capacity is reduced to some extent, so that the pressure fluctuation due to the time control operation can be suppressed, and the comfort during the operation of the refrigeration / air-conditioning apparatus can be ensured.

In the case where two compressors 1a and 1c which can be operated with stepwise capacities are provided as in the present embodiment, one of the compressors in the short cycle has the larger step. During at least a part of the time when the operation of the one capacity is performed, the other compressor performs the operation of the smaller capacity of the stage and the other compressor performs the operation of the larger capacity of the stage If one of the compressors is operated to operate at the smaller capacity of the stage at least for a part of the time, the state that both compressors 1a and 1c operate at the larger capacity becomes a short cycle. Pressure fluctuation can be reduced rather than overlapping for a long time.

FIG. 12 shows how the short period time is distributed. In FIG. 10, the operation with the large capacity and the operation with the small capacity of the compressors 1a and 1c are operated at the same timing, but in FIG. 12, this timing is shifted in the time direction. Therefore, looking at the operating capacity, at T1 in the short cycle, one of the compressors 1a has the larger capacity (6H).
At least a part of the time during which the operation P) is performed, the other compressor 1c is operating with the smaller capacity (2HP). At the same time, in T2 of the short cycle, at least part of the time when the other compressor 1c operates with the larger capacity (4HP), one of the compressors 1a has the smaller capacity (4HP). Drive. As a result, the fluctuation of the operating capacity becomes 8HP-10HP-8HP-6.
HP. By operating in this manner, the temporal fluctuation width of the operating capacity is reduced to some extent as compared with the operation as shown in FIG. Can be secured.

Further, in the present embodiment, the description has been made as to a configuration basically provided with two compressors which can be operated with stepwise capacity. However, three compressors which can be operated with stepwise capacity. The same effect can be obtained in the case of using the above. In terms of the effect that the pressure fluctuation of the refrigeration cycle can be reduced, the greater the number of capacity stages of the compressor that can be operated with stepwise capacity, the smaller the difference in capacity that can be switched in a short cycle than the smaller number of capacity stages. Is effective. In addition, a larger number of compressors is more effective than a small number of compressors, because the difference in capacity of switching in a short cycle can be reduced.

In the first and second embodiments,
Although the compressors 1a and 1c have been described as scroll compressors provided with bypass capacity control means, similar effects can be obtained by using the rotary compressors described in the related art as the compressors 1a and 1c. Further, the rotation speed of the compressor may be changed stepwise in a short cycle by a pole change of the motor. Further, even when reciprocating compressors are used as the compressors 1a and 1c and the number of operating cylinders is changed stepwise in short cycles, the same effects as those of the above embodiments can be obtained.

Embodiment 3 Hereinafter, as a refrigeration / air-conditioning apparatus according to Embodiment 3 of the present invention, for example, an apparatus for performing indoor air conditioning will be described. FIG. 13 is a refrigerant circuit diagram showing a configuration of the refrigeration / air-conditioning apparatus according to the present embodiment. In the figure,
Reference numeral 16 denotes a refrigerant container provided on the high pressure side of the refrigeration cycle, and reference numeral 17 denotes a refrigerant container provided on the low pressure side of the refrigeration cycle. The other elements in FIG. 13 and the flow of the refrigerant,
The method of switching the capacity of the compressor in FIG. 13 is the same as that in the first embodiment.

In this embodiment, at least one compressor 1a operable with a stepwise capacity is also provided. Further, as in the first embodiment, at least one compressor 1b having a constant capacity is provided, and a time control operation is performed in which the compressor 1a is operated at different stages of capacity at each time when a short cycle time distribution is allocated. Then, by changing the time distribution of the short cycle, the average capacity is changed, and the plurality of compressors 1 are changed.
The operating capacity can be arbitrarily and continuously changed as a and a as a whole. By performing the capacity control in this manner, the compressors 1a and 1b can be operated with a continuous capacity without using an inverter that adversely affects other devices due to harmonics. By the time control operation of the compressor 1a, the pressure pulsation width generated on the refrigeration cycle, the fluctuation width of the heat exchange amount in the heat exchanger, and the fluctuation of the outlet air temperature when the air heat exchanger is used as the heat exchanger And the like are caused by the stepwise switching of the operating capacity in the compressor 1a, and are caused by fluctuations in the flow rate of the refrigerant sucked or discharged into the compressor 1a.

Here, the situation of occurrence of fluctuation will be first focused on the high pressure side. Considering the high pressure side of the refrigeration cycle as one container, it is assumed that the refrigerant discharged from the compressors 1a and 1b flows into the high pressure side container. When the operating capacity of the compressor 1a increases and the flow rate of the refrigerant discharged from the compressor 1a increases, the flow rate of the refrigerant flowing into the high-pressure side container increases. At this time, since the amount of the refrigerant existing in the high-pressure side container increases, the density of the refrigerant in the container also increases, and the pressure in the container increases. Conversely, the operating capacity of the compressor 1a decreases, and the compressor 1a
When the flow rate of the refrigerant discharged from the outlet decreases, the flow rate of the refrigerant flowing into the high-pressure side container decreases. At this time, since the amount of the refrigerant present in the high pressure side container decreases, the density of the refrigerant in the container also decreases, and the pressure in the container decreases.

[0086] The situation of occurrence of fluctuation on the low pressure side can be grasped in a similar manner. Considering that the low pressure side of the refrigeration cycle is regarded as one container, the refrigerant drawn into the compressors 1a and 1b flows out of the low pressure side container. Think. When the operating capacity of the compressor 1a increases and the flow rate of the refrigerant sucked into the compressor 1a increases, the flow rate of the refrigerant flowing out of the low-pressure side container increases. At this time, since the amount of the refrigerant present in the low-pressure side container decreases, the density of the refrigerant in the container also decreases, and the pressure in the container also decreases. Conversely, the operating capacity of the compressor 1a decreases, and the compressor 1a
When the flow rate of the refrigerant sucked into the tank decreases, the flow rate of the refrigerant flowing out of the low-pressure side container decreases. At this time, since the amount of the refrigerant existing in the low-pressure side container increases, the density of the refrigerant in the container also increases, and the pressure in the container increases.

As described above, the fluctuation in the pressure is caused by the fluctuation in the amount of the refrigerant in the container causing the fluctuation in the density of the refrigerant in the container. Focusing on the fact that the density of the refrigerant in the container can be expressed by the amount of the refrigerant in the container / the volume of the container. It can be seen that the fluctuation width can be reduced. In the present embodiment, based on the above phenomenon, the refrigerant container 16 on the high pressure side or the refrigerant container 1 on the low pressure side of the refrigeration cycle is used.
By providing 7 or both, the volume on the high pressure side of the refrigeration cycle is equal to or more than the first predetermined volume, or the volume on the low pressure side is equal to or more than the second predetermined volume.

Next, the capacity of the high-pressure side container 16 and the low-pressure side container 17 will be described. The volume [L] of the container on the high pressure side or the low pressure side, the operation capacity fluctuation width [HP] in the time control operation,
Pressure fluctuation generated on the refrigeration cycle [kg / cm
² ], the four parameters of the short cycle length [sec] in the time control operation are related to each other. For example, when determining the volume of the low-pressure side or the high-pressure side vessel when designing a refrigeration / air-conditioning system, If the values of the other three parameters are determined, the volume can be determined. However, the equipment constituting the high-pressure side container includes compressor discharge pipes 2a and 2b, high-pressure side container 16-four-way valve 4-condenser (the outdoor heat exchanger 5 in the cooling operation).
In the heating operation, each of the indoor heat exchangers 8a and 8b) -the expansion valves 7a and 7b and the pipes connecting these components. On the other hand, the equipment constituting the low pressure side container is an expansion valve 7a,
7b—Evaporator (the indoor heat exchangers 8a and 8b in the cooling operation, and the outdoor heat exchanger 5 in the heating operation) —the four-way valve 4—the low-pressure side container 17—the compressor suction pipes 3a and 3b, and It is a pipe to be connected. As described in the first embodiment, the length of the short cycle [sec] in the time control operation is determined by the pressure fluctuation width, the fluctuation width of the blown air temperature when the air heat exchanger is used as the heat exchanger, and the like. Can be For example, when the air heat exchanger is used as the heat exchanger in order to ensure the comfort during the operation of the refrigeration air conditioner, the fluctuation range of the blown air temperature is 1 ° C.
When you Osaeyo the extent, pressure fluctuation range of the refrigeration cycle is 2 kgf / cm ² at high pressure, it is necessary to set the following order of 1 kgf / cm ² at low pressure. The length of the short cycle [sec] for suppressing the pressure fluctuation width varies depending on the operation capacity fluctuation width [HP] in the time control operation, but in general refrigeration cycles, it is set at intervals of approximately several seconds to several tens of seconds. Is done. In addition, the operating capacity fluctuation width [HP] in the time control operation
Means that the minimum capacity is 0.3HP or more, the maximum capacity is about 2 to 3 times the minimum capacity, and the variable width (maximum capacity-minimum capacity)
Is set to 1/10 to 1 times. In addition, the minimum volume of each device and piping required to configure the refrigeration / air-conditioning apparatus can be calculated or estimated in advance, and the high-pressure side container 16 or the low-pressure side container 17 can be calculated or estimated.
Is equal to or larger than the volume obtained by subtracting the minimum required volume of each device and piping from the volume of the low-pressure side or high-pressure side container determined by determining the other three parameters of the above four parameters. Just fine. Here,
The method of determining the volume by determining other parameters other than the volume among the four parameters has been described. However, the present invention is not limited to this. If the values of at least three parameters among the four parameters are determined, the remaining If it is used when designing a refrigeration / air-conditioning system, it is effective to obtain a device with high comfort.

The procedure for actually determining the volumes of the high-pressure side container 16 and the low-pressure side container 17 will be described. In FIG. 14, the horizontal axis shows the operation capacity control interval, which is the length of the short cycle in the time control operation, and the vertical axis shows {volume (L) of equipment and piping constituting the high pressure side} / operating capacity fluctuation width [ HP],
In FIG. 15, the horizontal axis shows the operation capacity control interval which is the length of the short cycle in the time control operation, and the vertical axis shows {volume (L) of equipment and piping constituting the low pressure side} / operating capacity fluctuation width [ HP]
FIG. The curve on the graph is shown in FIG.
In each case, the pressure fluctuation width of the refrigeration cycle is 1 kg / cm
² , 2 kg / cm ² and 3 kg / cm ² , and in FIG. 15, the pressure fluctuation width of the refrigeration cycle is 0.5 kg / c.
m ² , 1 kg / cm ² and 2 kg / cm ² .

The relationship between FIG. 14 and FIG.
It was obtained by Based on this relationship,
To keep the operation capacity control interval and pressure fluctuation width below a certain value
To determine the volume of the low pressure side or high pressure side vessel required for
Will be described. As described above, during operation of the refrigeration air conditioner
Use an air heat exchanger for the heat exchanger to ensure the comfort of
The fluctuation range of the blown air temperature when
If you try, the pressure fluctuation range of the refrigeration cycle is 2 kg at high pressure
f / cm^Two , 1kgf / cm at low pressure ^Two Set below
Need to be

Therefore, the pressure fluctuation range of the high pressure is set to 2 kgf / cm
^When the operation capacity control interval is set to ² and the operation capacity control interval is set to 10 seconds, the high pressure side volume [L] / operating capacity fluctuation width [HP] = 4 from FIG. Assuming 2HP, the required high pressure side volume is 8L. This value is the first predetermined volume. Therefore, the capacity of the high-pressure side container 16 is set in consideration of the volume of each device and piping constituting the high-pressure side so that the volume on the high-pressure side is 8 L or more. Similarly, when the pressure fluctuation width of the low pressure is suppressed to about 1 kgf / cm ² , the operation is performed at an operation capacity control interval of 10 seconds, and from FIG. Therefore, if the fluctuation range of the operating capacity of the compressor is 2HP, the required low-pressure side volume is 25
L. This value is the second predetermined volume. Therefore, the capacity of the low-pressure side container 17 is set in consideration of the volume of each device and the pipe constituting the low-pressure side so that the volume on the low-pressure side becomes 25 L or more.

As described above, the first predetermined volume or the second predetermined volume is defined as the allowable value of the high-pressure side or low-pressure side pressure fluctuation width generated in the refrigeration cycle by the operation of the compressor, the short cycle length, and the short cycle length. With the determination based on the operating capacity fluctuation width of the compressor in the cycle, the volume on the high pressure side or the low pressure side can be set so as to satisfy the operating conditions, the configuration of the devices, and the comfort when using the device. Also, the container 1 is placed on the high pressure side or the low pressure side.
By providing 6, 17, the fluctuation of the density of the refrigerant is reduced even if the operating capacity of the compressor fluctuates, and the fluctuation range on the refrigeration cycle such as the pressure fluctuation accompanying the fluctuation of the operating capacity of the compressor is suppressed. In addition, fluctuations in refrigeration capacity and air conditioning capacity, such as fluctuations in the temperature of blown air, are reduced, and there is an effect that comfort during operation of the refrigeration air conditioner can be secured.

In FIG. 13, the high-pressure side container 16 is provided on the compressor discharge side, and the low-pressure side container 17 is provided on the compressor suction side.
In the high-pressure portion of the refrigeration cycle from the discharge ports of the compressors 1a and 1b until the pressure is reduced by the expansion valve 7, the compressor 1
The same effect can be obtained even if it is installed in any part of the part before it is sucked into a and 1b.

Further, here, the volume on both the high-pressure side and the low-pressure side is configured to be equal to or more than a predetermined value. Yes, but it works.

In order to suppress pressure fluctuation, the container 1
In addition to the configuration in which 6, 17 are provided, the volume of each of the high-pressure side and the low-pressure side may be increased. For example, the pipe diameter of the extension pipe connecting the outdoor unit and the indoor unit may be increased, the pipe length may be increased, and the compressor 1a, 1
The diameter of the pipe connecting the b and the outdoor heat exchanger 5 may be increased, or the length of the pipe may be increased. Further, the diameter of the heat transfer tubes used in the indoor heat exchangers 8a and 8b and the outdoor heat exchanger 5 may be increased, or the length of the heat transfer tubes may be increased. In any configuration, the volume of each of the high-pressure side and the low-pressure side can be increased.

As described above, also in this embodiment, by operating without using an inverter, there is no adverse effect of harmonics caused by using an inverter. Furthermore, the compressor 1b is provided separately from the compressor 1a that can be operated with a stepwise capacity, and the capacity fluctuation width in the time control operation can be reduced. Further, the total volume of the internal volume of at least one of the high-pressure side and the low-pressure side of the refrigeration cycle is set to a predetermined value or more so as to reduce the pressure fluctuation width of the refrigeration cycle, so that the compressor can be operated with a stepwise capacity. In 1a, the pressure pulsation width generated on the refrigeration cycle due to the capacity fluctuation when the time control operation is performed, the fluctuation width of the heat exchange amount in the heat exchanger, the blowout when the air heat exchanger is used as the heat exchanger The fluctuation range of the air temperature can be reduced. For this reason, the fluctuation | variation of the refrigerating capacity or air conditioning capacity in a refrigerating air conditioner can be made small, and the refrigerating air conditioner which can ensure the comfort at the time of driving | operation can be obtained.

Embodiment 4 Hereinafter, as a refrigeration / air-conditioning apparatus according to Embodiment 4 of the present invention, for example, an apparatus for performing indoor air-conditioning will be described. In this embodiment, similarly to Embodiment 3, a container is provided on at least one of the high pressure side and the low pressure side of the refrigeration cycle to increase the volume on the high pressure side or the low pressure side. With this, the pressure pulsation width generated on the refrigeration cycle due to the time-controlled operation of the compressor that can be operated in stepwise capacity, the fluctuation width of the heat exchange amount in the heat exchanger, the air heat exchanger to the heat exchanger Is used to reduce the fluctuation range of the blow-off air temperature and the like to reduce the fluctuation of the refrigeration capacity or the air conditioning capacity of the refrigeration / air-conditioning apparatus. Further, in this embodiment, in addition to increasing the volume on the high-pressure side or the low-pressure side to suppress pressure fluctuation, other functions that are effective in configuring the refrigeration cycle as the high-pressure side vessel or the low-pressure side vessel A container which also has a function is provided.

FIG. 16 is a refrigerant circuit diagram showing the configuration of the refrigeration / air-conditioning apparatus according to the present embodiment. In the drawing, reference numeral 17 denotes a low-pressure side container, reference numeral 18 denotes an oil separator, and reference numeral 19 denotes an oil return circuit for returning the oil separated by the oil separator 18 to the compressor suction side. The other configuration in FIG. 16, the flow of the refrigerant, and the method of switching the capacity of the compressor in FIG. 16 are the same as those in the first embodiment.

The compressors 1a and 1b are usually filled with lubricating oil for smooth operation of each member. Part of this oil is discharged from the compressors 1a and 1b together with the gas refrigerant, and circulates in the refrigeration cycle together with the refrigerant. However, if this oil accumulates in the liquid pipe 6 and gas pipe 9 during circulation,
The amount of oil in the compressors 1a and 1b decreases without returning to the compressors 1a and 1b. When the amount of oil that causes each member in the compressors 1a and 1b to operate smoothly decreases, the operations of the compressors 1a and 1b are not performed smoothly. In the present embodiment, the compressor 1
a, an oil separator 18 is provided in the discharge-side piping of 1b,
The oil separator 18 allows the compressors 1a, 1b
By separating the oil discharged from the compressor together with the gas refrigerant and returning the oil to the suction side of the compressors 1a and 1b via the oil return circuit 19,
The situation where the compressors 1a and 1b are damaged can be avoided. Further, by increasing the volume on the high pressure side by the amount of the oil separator 18, it is possible to suppress the pressure fluctuation in the time control operation of the compressor 1a that can be operated with the stepwise capacity.

Thus, the function of increasing the volume on the high pressure side by the oil separator 18 and the function of the compressors 1a, 1a
It also has the function of returning the oil discharged from b. For this reason, the fluctuation range of the pressure due to the time control operation of the compressor 1a can be suppressed, the comfort at the time of operating the refrigeration air conditioner can be secured, and the reliability at the time of operating the compressors 1a and 1b can be improved. it can. Normally, assuming that the volume of the oil separator 18 is about 3 L and each high-pressure side device and piping constituting the refrigeration cycle is about 5 L, according to FIG. ) Is 10 seconds, the pressure fluctuation width can be reduced to about 2 kg / cm ² . Thus, by providing the oil separator 18 on the discharge side of the compressors 1a and 1b,
Comfort during operation of the refrigeration / air-conditioning apparatus can be ensured, and reliability during operation of the compressor can be improved.

A liquid receiver 30 may be provided at the outlet of the outdoor heat exchanger 5 as shown in FIG. The outdoor heat exchanger 5 operates as a condenser when the refrigeration / air-conditioning apparatus performs a cooling operation. By providing the liquid receiver 30 at the outlet of the condenser, the amount of the refrigerant in the refrigeration / air-conditioning apparatus is adjusted, and the optimum state of the operation of the refrigeration cycle is achieved. Further, since the excess refrigerant in the refrigeration cycle can be retained, even if there is excess refrigerant in the refrigeration cycle, the liquid does not return to the compressors 1a and 1b, and damage to the compressor due to liquid compression can be avoided. . Further, by providing the liquid receiver 30, the volume on the high pressure side is increased in the cooling operation, and the fluctuation range of the pressure generated by performing the time control operation of the compressor 1a that can be operated with the stepwise capacity is suppressed. I do. As described above, by providing the liquid receiver 30 at the outlet of the heat exchanger that operates as a condenser, it is possible to ensure comfort during operation of the refrigeration / air-conditioning apparatus and improve reliability when operating the compressor. Can be. When the liquid receiver 30 is connected as shown in the drawing, there is an effect of increasing the volume on the low pressure side when switching to the heating operation.

As shown in FIG. 18, an accumulator 31 may be provided on the suction side of the compressors 1a and 1b. By providing the accumulator 31, the liquid refrigerant flowing to the compressor suction side during the start-up operation in the refrigeration / air-conditioning apparatus is retained in the accumulator 31, so that the operation returns to the compressors 1a and 1b at the start-up. Compressor 1a, 1b by liquid compression
Can be avoided and reliability can be improved. Further, by providing the accumulator 31, the volume on the low pressure side of the refrigeration cycle can be increased, and the fluctuation range of the pressure generated by performing the time control operation of the compressor 1a can be suppressed. Thus, by providing the accumulator 31 on the suction side of the compressors 1a and 1b on the low pressure side of the refrigeration cycle, it is possible to ensure comfort during operation of the refrigeration and air conditioning system, And the reliability at the time of operating a compressor can be improved.

In FIGS. 16, 16 and 17, each refrigerating and air-conditioning system has an oil separator 18, a liquid receiver 30, and an accumulator 31. A configuration may be used. In addition, the oil separator 18, the liquid receiver 3
0, when the volume is not enough even with the configuration having the accumulator 31, as shown in FIG. Is also good.

Embodiment 5 FIG. Hereinafter, as a refrigeration / air-conditioning apparatus according to Embodiment 5 of the present invention, for example, an apparatus for performing indoor air conditioning will be described. FIG. 19 is a refrigerant circuit diagram showing a configuration of a refrigeration / air-conditioning apparatus according to the present embodiment. In the figure,
Reference numeral 32 denotes a resistance element provided on the discharge side of the compressor for adding a flow resistance. For example, a diameter of a part of a refrigerant pipe is made smaller than a diameter of another part to constitute a resistance element for the flow of the refrigerant. I have. Reference numeral 33 denotes a resistance element provided on the suction side of the compressor for adding flow resistance. For example, similarly to the resistance element 32, the diameter of a part of the refrigerant pipe is made smaller than the diameter of the other part to prevent the flow of the refrigerant. It constitutes a resistance element. The other configuration in FIG. 19, the flow of the refrigerant, and the method of switching the capacity of the compressor in FIG. 19 are the same as those in the first embodiment.

As described above, in the compressor 1a which can be operated with the stepwise capacity, the pressure pulsation generated on the refrigeration cycle when performing the time control operation causes the refrigerant to be sucked into and discharged from the compressor 1a. With the flow rate fluctuating in a short cycle, the flow rate of the refrigerant flowing into the high pressure side and the flow rate of the refrigerant flowing out from the low pressure side fluctuate in a short time. Occurs as a result of density fluctuations. Therefore, if fluctuations in the flow rate of the refrigerant flowing into the high-pressure side and the flow rate of the refrigerant flowing out of the low-pressure side can be suppressed, pressure pulsation occurring on the refrigeration cycle can be suppressed.

Therefore, in the present embodiment, a resistance element 32 and a resistance element 33 are provided on the discharge side and the suction side of the compressor 1a. Here, for example, the operation of the resistance element 32 provided on the discharge side of the compressor 1a will be described. When the time control operation is performed by the compressor 1a, and when the operation capacity is switched from the small capacity to the large capacity, the flow rate of the refrigerant discharged from the compressor 1a increases, and the increase is caused by the resistance element 32. , And then passes through the resistance element 32 and contributes to an increase in the flow rate of the refrigerant. Therefore, an increase in the amount of refrigerant on the high pressure side can be suppressed as compared with a case where the resistance element 32 is not provided. Further, in the time control operation of the compressor 1a, when the operation capacity is switched from the large capacity to the small capacity, the flow rate of the refrigerant discharged from the compressor 1a decreases, and as a result, the compression of the resistance element 32 is reduced. A pressure decrease occurs on the machine side, and the amount of refrigerant that passes through the resistance element 32 corresponds to the pressure decrease.
Therefore, a decrease in the amount of refrigerant on the high pressure side can be suppressed as compared with a case where the resistance element 32 is not provided. This operation is the same for the low-voltage side resistance element 33.

As described above, the resistance elements 32 and 33 are provided in the refrigerant passage.
Is provided, even if the flow rate of refrigerant sucked into and discharged from the compressor 1a fluctuates due to a change in the operating capacity of the compressor 1a,
Due to the flow resistance when the refrigerant passes through the resistance elements 32 and 33, the variation in the flow rate of the refrigerant becomes difficult to pass through the resistance elements 32 and 33. Therefore, fluctuations in the flow rate of the refrigerant flowing into the high pressure side and the flow rate of the refrigerant flowing out of the low pressure side are reduced by the compressor 1a.
Can be made smaller than the fluctuation of the flow rate of the refrigerant generated in the above. Therefore, the pressure pulsation generated on the refrigeration cycle can be suppressed, and the fluctuation width of the heat exchange amount in the heat exchanger, the fluctuation width of the outlet air temperature when the air heat exchanger is used as the heat exchanger, and the like can be reduced. Since it is possible to reduce the fluctuation of the refrigeration capacity or the air conditioning capacity in the refrigeration / air-conditioning apparatus, it is possible to ensure comfort during the operation of the refrigeration / air-conditioning apparatus.

In the structure shown in FIG. 19, the resistance elements 32 and 33 are provided on the high voltage side and the low voltage side, respectively. Preferably, the resistance elements 32 and 33 are provided on both sides, but the effect is large. Further, the resistance element that adds flow resistance may be of any configuration that adds flow resistance to the refrigerant flowing through the pipe, such as a throttle provided in a refrigerant pipe like a capillary.

Also, the resistance element 3 provided on the discharge side of the compressor
With respect to 2, a check valve may be provided that allows the flow in the direction from the compressors 1a and 1b to the four-way valve 4 to pass and blocks the flow in the opposite direction. By using the check valve as the resistance element 32 that adds the flow resistance to the flow of the refrigerant on the high pressure side, in addition to the effect of suppressing the pressure pulsation generated on the refrigeration cycle, the outdoor air conditioner is stopped while the refrigeration air conditioner is stopped. Through the four-way valve 4 from the heat exchanger 5 or the indoor heat exchangers 8a and 8b, it is possible to prevent the liquid refrigerant from flowing into the compressors 1a and 1b from the discharge sides of the compressors 1a and 1b. If the liquid refrigerant is allowed to flow into the compressors 1a and 1b during the stop, the liquid refrigerant flows into the compressors 1a and 1b when the refrigeration / air-conditioning system is to be started. This may cause damage to the compressors 1a and 1b. On the other hand, by providing the check valve 32, it is possible to prevent the liquid from flowing into the compressors 1a and 1b even when the refrigeration and air-conditioning system is stopped, and to prevent the compressor from being damaged due to the liquid compression, thereby providing more reliability. Highly operable driving becomes possible.

As shown in FIG. 20, the compressor 1a,
Similar effects can be obtained even if check valves 32a and 32b are provided as resistance elements in the discharge pipes 2a and 2b of 1b, respectively.

Embodiment 6 FIG. Hereinafter, as a refrigeration / air-conditioning apparatus according to Embodiment 6 of the present invention, for example, an apparatus for performing indoor air-conditioning will be described. FIG. 21 is a refrigerant circuit diagram illustrating a configuration of a refrigeration / air-conditioning apparatus according to the present embodiment. In the figure, reference numeral 34 denotes a bypass circuit, for example, a circuit connecting the discharge side of the compressor and the suction side of the compressor, and 35 a control valve for controlling the flow rate of the refrigerant flowing through the bypass circuit 34. The other configuration of FIG. 21, the flow of the refrigerant, and the method of switching the capacity of the compressor in FIG. 21 are the same as those in the first embodiment.

As described above, in the compressor 1a which can be operated in a stepwise capacity, the pressure pulsation generated on the refrigeration cycle when performing the time control operation causes the refrigerant to be sucked into and discharged from the compressor 1a. By the flow rate fluctuating in a short cycle, the flow rate of the refrigerant flowing into the high pressure side and the flow rate of the refrigerant flowing out from the low pressure side fluctuate in a short time, and the amount of the refrigerant present on the high pressure side and the low pressure side fluctuates accordingly. Occurs by causing density fluctuations. Therefore, if fluctuations in the flow rate of the refrigerant flowing into the high-pressure side and the flow rate of the refrigerant flowing out of the low-pressure side can be suppressed, pressure pulsation occurring on the refrigeration cycle can be suppressed.

Therefore, in the present embodiment, in the compressor 1a, when performing the time control operation, the control valve 35 is opened so that the refrigerant flows from the discharge sides of the compressors 1a and 1b to the suction side. The control valve 35 is closed when the compressor 1a is stopped or performs a constant capacity operation in a short cycle. Compressor 1a
When the time control operation is performed at the time, when the operation capacity is switched from the capacity of the small stage to the capacity of the large stage,
The flow rate of refrigerant sucked and discharged into the compressor 1a increases,
The amount of refrigerant existing on the high pressure side increases and the high pressure increases, and the flow rate of refrigerant flowing out from the low pressure side also increases, and the low pressure decreases. Therefore, the pressure difference between the high pressure and the low pressure increases. When the pressure difference increases, the flow rate of the refrigerant flowing through the bypass circuit 34 increases. An increase in the flow rate of the refrigerant flowing through the bypass circuit 34 means that the flow rate of the refrigerant flowing out of the high pressure side and the flow rate of the refrigerant flowing into the low pressure side both increase. Thus, it is possible to suppress an increase in the amount of refrigerant existing on the high pressure side and a decrease in the amount of refrigerant existing on the low pressure side. As described above, fluctuations in the amounts of the refrigerant present on the high pressure side and the low pressure side can be suppressed, so that pressure pulsation generated on the refrigeration cycle can be suppressed.

When the operation capacity is switched from the large capacity to the small capacity in the time control operation of the compressor 1a, the flow rate of the refrigerant sucked and discharged to the compressor 1a is reduced, and the flow rate of the refrigerant existing on the high pressure side is reduced. The amount of refrigerant flowing decreases, the high pressure decreases, the flow rate of refrigerant flowing out from the low pressure side also decreases, and the low pressure increases. Therefore, the pressure difference between the high pressure and the low pressure decreases. As the pressure difference decreases, the flow rate of the refrigerant flowing through the bypass circuit 34 decreases. Decreasing the flow rate of the refrigerant flowing through the bypass circuit 34 means that the flow rate of the refrigerant flowing out of the high-pressure side and the flow rate of the refrigerant flowing into the low-pressure side both decrease. Thus, it is possible to suppress a decrease in the amount of refrigerant existing on the high pressure side and an increase in the amount of refrigerant existing on the low pressure side. As described above, fluctuations in the amounts of the refrigerant present on the high pressure side and the low pressure side can be suppressed, so that pressure pulsation generated on the refrigeration cycle can be suppressed.

As described above, in this embodiment, the bypass circuit 34 and the control valve 35 are provided, and the high pressure side and the low pressure side of the refrigeration cycle are connected when the time control operation is performed by the compressor 1a. An appropriate amount of refrigerant that automatically reduces the fluctuation of the refrigerant amount due to the pressure fluctuation generated during the time control operation flows through the bypass circuit 34, the pressure pulsation width generated on the refrigeration cycle by the time control operation, and the heat exchanger. , The fluctuation range of the blown air temperature when the air heat exchanger is used as the heat exchanger, and the like. Therefore, fluctuations in the refrigeration capacity or air conditioning capacity of the refrigeration / air-conditioning apparatus can be reduced, and comfort during operation of the refrigeration / air-conditioning apparatus can be ensured.

The high pressure side and the low pressure side may always be connected by the bypass circuit 34 without providing the control valve 35.
At this time, the bypass circuit 34 changes the flow rate of the refrigerant in the main piping constituting the refrigeration cycle from 1/100 to 10/1.
It is desirable to make a configuration such that about 00 refrigerant flows.
Of course, flowing the refrigerant to the bypass circuit 34 connecting the discharge side and the suction side of the compressor means that a part of the flow rate of the compressor is not used for the cooling capacity or the heating capacity of the refrigerating air conditioner. Decreases cycle operation efficiency. Therefore, when the time is not controlled by the compressor 1a by the control valve 35, this bypass circuit 3
By closing 4, the operation efficiency of the refrigeration cycle can be prevented from lowering.

Further, by forming the bypass circuit 34 as a circuit for connecting the discharge side and the suction side of the compressor, when the load of the refrigeration / air-conditioning apparatus is increased, or when the heat exchanger serving as the condenser becomes abnormal, Accordingly, when the high pressure rises excessively, the control valve 35 is opened to allow the refrigerant to flow through the bypass circuit 34, thereby suppressing the excessive rise of the high pressure. By bypassing the high-pressure refrigerant to the low-pressure side by the bypass circuit 34, it is possible to prevent the compressor from being damaged due to an excessive rise in high-pressure,
In addition to suppressing the pressure pulsation that occurs on the refrigeration cycle, the reliability of the operation of the refrigeration air conditioner can be improved.

Further, as shown in FIG. 16, the bypass circuit 34 may be used also as the oil return circuit 19 for returning the oil separated by the oil separator 18 to the compressor suction side. By using the oil separator 18, in addition to the above-described effects, lubricating oil in the compressor flowing out together with the gas refrigerant from the discharge sides of the compressors 1a and 1b can be returned to the compressor. Malfunction and damage can be prevented, and the reliability of the refrigeration and air conditioning system can be improved.

Further, the bypass circuit 34 connecting the high pressure side and the low pressure side is not limited to the bypass circuit 34 connecting the discharge side and the suction side of the compressor, and may have another configuration. FIG. 22 is a refrigerant circuit diagram showing another configuration of the refrigeration and air-conditioning apparatus according to the present embodiment. In this configuration, one end of the bypass circuit 34 is connected to the liquid pipe 6 between the outdoor heat exchanger 5 and the expansion valves 7a, 7b, and the other end of the bypass circuit 34 is connected to the suction pipes 3a, 3b of the compressor. ing. With this configuration, during the cooling operation, the outdoor heat exchanger 5 operates as a condenser. Therefore, the outlet of the outdoor heat exchanger 5 on the high-pressure side is connected to the compressor suction side on the low-pressure side. The generated pressure pulsation can be suppressed. In addition, when connected in this manner, the liquid refrigerant condensed in the outdoor heat exchanger 5 during the cooling operation is supplied to the compressor 1.
a, 1b. For example, during operation, the compressor 1
When the discharge temperatures of the compressors 1a and 1b rise, the control valve 35 is opened to return the liquid refrigerant to the compressors 1a and 1b, whereby the rise of the discharge temperature can be suppressed. It is possible to increase. The control valve 35 in FIG. 22 and FIG.

FIG. 23 is a refrigerant circuit diagram showing still another configuration of the refrigeration / air-conditioning apparatus according to the present embodiment. In the figure, reference numeral 36 denotes a heat exchange unit for exchanging heat between the bypassed liquid refrigerant and the high-pressure liquid refrigerant, for example, a high-low pressure heat exchanger. The control valve 35 having this configuration has a pressure reducing function. The liquid refrigerant flowing through the bypass circuit 34 during the cooling operation is:
The pressure is reduced by the control valve 35 to become a low-pressure low-temperature two-phase refrigerant. By exchanging heat between the two-phase refrigerant and the high-pressure and high-temperature liquid refrigerant flowing through the liquid pipe 6 in the high-low pressure heat exchanger 36, the low-pressure two-phase refrigerant is vaporized and gasified. Therefore, in addition to suppressing the pressure pulsation generated on the refrigeration cycle by the bypass circuit 34, the latent heat of evaporation of the bypassed liquid refrigerant can be recovered, and the cooling capacity is reduced by bypassing the liquid refrigerant during the cooling operation. Can be reduced. Furthermore, during the cooling operation, the outdoor heat exchanger 5 switches to the indoor heat exchangers 8a and 8b.
Since the flow rate of the refrigerant flowing through the gas pipe 9 can be reduced without lowering the cooling capacity, the pressure loss generated in the gas pipe 9 can be reduced, and the refrigeration / air-conditioning apparatus can be operated with higher efficiency.

Embodiment 7 FIG. Hereinafter, as a refrigeration / air-conditioning apparatus according to Embodiment 7 of the present invention, for example, an apparatus for performing indoor air-conditioning will be described. FIG. 24 is a refrigerant circuit diagram showing a configuration of the refrigeration / air-conditioning apparatus according to the present embodiment. In the present embodiment, as shown in the figure, an oil return circuit 19 for the oil separated by the oil separator 18 is connected to the high-pressure solenoid valve 10a, and the oil separated by the oil separator 18 is supplied to the high-pressure solenoid valve 10a. I do. When this is opened, it is supplied to the low-pressure side solenoid valve 10b through the high-pressure side solenoid valve 10a. The supplied oil flows into the low pressure side solenoid valve 10b,
Thereafter, when it is opened, it passes through the low pressure side solenoid valve 10b and returns to the compressor suction side. The other configuration in FIG. 24, the flow of the refrigerant, and the method of switching the capacity of the compressor in FIG. 24 are the same as those in the first embodiment.

As in the present embodiment, switching of the operation capacity of the compressor 1a is performed by switching the high-pressure side solenoid valve 10 which is two control valves.
a) When the operation is performed by opening and closing the low-pressure side solenoid valve 10b, the number of opening and closing of each solenoid valve increases. For example, the time for operating the compressor 1a at the maximum capacity and the time for operating at the minimum capacity are considered as one set. When the operation time of the compressor 1a is 25,000 hours, the number of times of opening and closing of each of the solenoid valves 10a and 10b is 9 million, which is considerably higher than the serviceable number of times of the general solenoid valve of several hundred thousand times. The number of times of opening and closing is required.

FIG. 25 shows the solenoid valve 10 according to this embodiment.
It is sectional drawing which shows the structure of a and 10b. In the figure, 3
7 is a movable valve, 38 is a valve seat, 39 is a plunger, 40 is a coil, 41 is a valve inlet side flow path, and 42 is a valve outlet side flow path. The operation of the solenoid valves 10a and 10b is as follows.
When the valve is opened, a current flows through the coil 40, and a magnetic force is generated from the movable valve 37 to the plunger 39 by the electromagnetic force, so that the movable valve 37 is attracted to the plunger 39. When the plunger 39 moves upward in the figure,
A gap is formed between the movable valve 37 and the valve seat 38, the valve inlet side flow path 41 and the valve outlet side flow path 42 communicate, and the valve is in an open state. When the valve is closed, no current flows through the coil 40. Then, the magnetic force from the movable valve 37 to the plunger 39 disappears, and the force for attracting the movable valve 37 to the plunger 39 disappears. For this reason, while the plunger 39 moves downward in the drawing, the pressure of the flowing refrigerant is higher on the valve inlet side 41 than on the valve outlet side 42, so that the movable valve 37 is pressed against the valve seat 38 by the refrigerant pressure difference. . By doing so, the gap between the movable valve 37 and the valve seat 38 is eliminated, and the space between the valve inlet side flow path 41 and the valve outlet side flow path 42 is closed.

Therefore, each time the solenoid valves 10a and 10b are opened and closed, the plunger 39 collides with the movable valve 37 and the movable valve 37 collides with the valve seat 38.
Plunger 39 and movable valve 3
7, wear of the valve seat 38 and the like progresses. In particular, there is a possibility that a gap may be formed between the movable valve 37 and the valve seat 38 due to the wear, so that the valve cannot be completely closed. Therefore, in the present embodiment, the movable valve 37
The oil separated by the oil separator 18 is supplied to the solenoid valves 10a and 10b in order to prevent the wear of the valve seat 38 and the valve seat 38 and to secure a predetermined service life. By supplying oil to the solenoid valves 10a and 10b, a contact portion between the movable valve 37 and the valve seat 38, a contact portion between the plunger 39 and the movable valve 37, a sliding portion between the movable valve 37 and the inner surface of the container, and the like are provided. An oil film is formed. The oil film serves as an impact mitigation means for alleviating an impact in a collision at a portion where the solenoid valves 10a and 10b contact by opening and closing, for example, a contact portion between the movable valve 37 and the valve seat 38. Part wear can be prevented.

The oil film can be formed with a small amount of oil, and when the amount of oil taken out from the compressors 1a and 1b is large,
In some cases, the amount of oil supplied to the solenoid valves 10a and 10b becomes too large. If the amount of oil supplied to the solenoid valves 10a and 10b is too large and the inside of the solenoid valves 10a and 10b is filled with oil, the viscosity of the oil is larger than that of the refrigerant.
0a and 10b, the amount of oil in the solenoid valve 10 increases.
More electromagnetic force is required for opening and closing a and 10b. Therefore, if the solenoid valves 10a and 10b are designed to be opened and closed when a refrigerant is used, the electromagnetic valves 10a and 10b cannot be opened and closed sufficiently due to insufficient electromagnetic force when oil is filled in the valves. As a result, the capacity control of the compressor may not be able to be performed. Therefore, when supplying oil to the solenoid valves 10a and 10b, it is necessary to supply an optimal amount of oil to the solenoid valves 10a and 10b.

Therefore, in the present embodiment, the solenoid valves 10a,
Various configurations are provided for the state of the oil when the oil is supplied to 10b. First, in the configuration shown in FIG.
The oil that has flowed out of the compressor together with the refrigerant gas is separated by an oil separator 18, and oil free of refrigerant is separated from the solenoid valve 10.
a and 10b. In this case, the solenoid valves 10a, 1
The amount of oil supplied to Ob is relatively large.

In the configuration shown in FIG. 26, the compressor 1
a, 1b and the oil separator 18 by connecting the compressor discharge side and the high pressure side solenoid valve 10a, the solenoid valve 10a,
The refrigerant gas before passing through the oil separator 18 is supplied to 10b. In this case, the amount of oil supplied to the solenoid valves 10a and 10b is determined by setting the oil return circuit 19 of the oil separator 18 to the solenoid valve 1
0a, that is, less than the configuration shown in FIG. This is because the refrigerant gas before passing through the oil separator 18 is supplied, so that the solenoid valves 10a, 10b
Is supplied with the refrigerant gas together with the oil, and the amount of oil is smaller than when the separated oil is supplied.

In the structure shown in FIG. 27, the compressor discharge side between the oil separator 18 and the four-way valve 4 and the high-pressure side solenoid valve 10a are connected to allow the solenoid valves 10a and 10b to pass through the oil separator 18 Is supplied. In this case, since oil contained in the refrigerant gas is removed by the oil separator 18, the amount of oil supplied to the solenoid valves 10a and 10b depends on the configuration of supplying the refrigerant gas before passing through the oil separator 18, that is, as shown in FIG. Less than that of the configuration. However, since the oil contained in the refrigerant gas cannot be completely removed by the oil separator 18, even if the refrigerant gas after passing through the oil separator 18 is supplied, a small amount of oil can be supplied. The amount of the supplied oil greatly depends on the performance of the oil separator 18.

As shown in FIGS. 24, 26 and 27, the amount of oil supplied to the solenoid valves 10a and 10b can be increased or decreased.
The configuration may be selected according to the outflow state of the oil from the compressors 1a and 1b, the properties of the oil and the refrigerant, the performance of the oil separator, and the like. For example, when the amount of oil taken out of the compressors 1a and 1b is too large, as shown in FIG.
When the oil return circuit 19 of FIG. 8 is connected to the solenoid valve 10a, there is a possibility that the inside of the solenoid valves 10a and 10b is filled with oil. At this time, as shown in FIG.
Supply the refrigerant gas before 8 passes. Further, even if the refrigerant gas before passing through the oil separator 18 is supplied as shown in FIG.
When oil fills the solenoid valves 10a and 10b, the refrigerant gas after passing through the oil separator 18 may be supplied as shown in FIG.

Conversely, when the amount of oil taken out of the compressors 1a and 1b is small, when the refrigerant gas after passing through the oil separator 18 is supplied to the solenoid valve 10a as shown in FIG.
There is a possibility that an oil film for an impact reducing action cannot be formed at a contact portion such as the surface of the movable valve 37 and the valve seat 38. At this time, the refrigerant gas before passing through the oil separator 18 is supplied to the solenoid valve 10a as shown in FIG. When an oil film cannot be formed on the surfaces of the movable valve 37 and the valve seat 38 even if the refrigerant gas before passing through the oil separator 18 is supplied as shown in FIG. 26, the oil return circuit 19 of the oil separator 18 as shown in FIG. May be connected to the solenoid valve 10a to supply the separated oil.

As described above, in the present embodiment, FIG.
4, the compressors 1a, 1b
The oil that has flowed out together with the refrigerant gas from the solenoid valves 10a and 10b
And then return to the compressors 1a and 1b. For this reason, an oil film is generated on the surface of the contact portion due to the opening and closing of the solenoid valves 10a and 10b, for example, the surfaces of the movable valve 37 and the valve seat 38 to reduce the impact, thereby preventing the contact portion from being worn.
Ensuring valve closing performance. 24, 26, and 27, the refrigeration and air-conditioning system is configured based on the amount of oil flowing out of the compressors 1a and 1b and the degree of oil film formation at the contact portion due to the nature of the oil. By selecting an optimal configuration, an appropriate amount of oil can be supplied to the solenoid valves 10a and 10b, and the valve can be reliably opened and closed without filling the inside of the solenoid valves with reliability. Can be secured.

Embodiment 8 FIG. Hereinafter, as a refrigeration / air-conditioning apparatus according to Embodiment 8 of the present invention, for example, an apparatus for performing indoor air conditioning will be described. In the present embodiment, the solenoid valves 10a, 10b, which are control valves for performing the time control operation of the compressor 1a,
The cooling means for cooling the b is provided to prevent the deterioration of each member due to the temperature rise of the expansion valves 10a and 10b. FIG. 28 is a refrigerant circuit diagram illustrating a configuration of a refrigeration / air-conditioning apparatus according to the present embodiment. In the figure, reference numeral 7c denotes an expansion valve, and 43 denotes a pipe for supplying a high-pressure liquid refrigerant to the solenoid valve 10a. The other configuration in FIG. 28 is the same as that in the first embodiment. In the first to seventh embodiments, the piping in which the refrigerant gas flows and the high-pressure side solenoid valve 10a are connected. However, in the configuration of FIG. 28, the piping in which the refrigerant liquid flows and the high pressure side solenoid valve 10a are connected. It has a configuration. By supplying the high-pressure liquid refrigerant to the solenoid valves 10a and 10b, the operation of controlling the operating capacity by opening and closing the solenoid valves 10a and 10b is not hindered, and the solenoid valves 10a and 10b are cooled. , 10b is supplied with the oil flowing with the refrigerant.

In this embodiment, the expansion valve 7c is provided at the outlet side of the outdoor heat exchanger 5 which operates as a condenser during the cooling operation, and the liquid pipe 6 between the expansion valve 7c and the expansion valves 7a and 7b.
And the high pressure side solenoid valve 10 a are connected by a pipe 43. Here, an expansion valve 7c is provided between the outdoor heat exchanger 5 and the expansion valves 7a and 7b.
Is provided so that high-pressure liquid refrigerant can be supplied to the solenoid valves 10a and 10b, which are control valves when performing the time control operation of the compressor 1a, in both the cooling operation and the heating operation. In the cooling operation, a part of the high-pressure liquid refrigerant condensed in the outdoor heat exchanger 5 is supplied to the solenoid valves 10a and 10b by fully opening the expansion valve 7c so as not to reduce the pressure. The refrigerant not supplied to the solenoid valves 10a and 10b is decompressed by the expansion valves 7a and 7b, and is supplied to the indoor heat exchangers 8a and 8b.
8b. Other refrigerant flows in the cooling operation and the method of switching the capacity of the compressor are the same as those in the first embodiment. On the other hand, in the heating operation, the indoor heat exchangers 8a, 8b
The refrigerant flows to the connection point of the pipe 43 that supplies the high-pressure liquid refrigerant condensed in the above to the solenoid valves 10a and 10b. Then, a part thereof flows to the pipe 43 and is supplied to the solenoid valves 10a and 10b.
The high-pressure liquid refrigerant that has not flown into the pipe 43 flows into the outdoor heat exchanger 5 after being decompressed by the expansion valve 7c. Other refrigerant flows in the heating operation and a method for switching the capacity of the compressor are the same as those in the first embodiment.

Also in the present embodiment, the switching of the operation capacity in the time control operation of the compressor 1a is performed by opening and closing the high-pressure side solenoid valve 10a and the low-pressure side solenoid valve 10b. The number of times of opening and closing 10b increases. When switching the operation capacity, the coils 4 of the solenoid valves 10a and 10b
Since the current flows continuously to zero, the amount of heat generated by the coil 40 increases, and the temperatures of the solenoid valves 10a and 10b themselves increase. When the temperature of the solenoid valves 10a and 10b rises, the materials of the solenoid valves 10a and 10b are easily deteriorated, and the malfunction of the solenoid valves 10a and 10b is easily caused. Therefore, in order to ensure the drive reliability of the solenoid valves 10a and 10b, the solenoid valves 10a and 10b need to be cooled.
In the present embodiment, a high-pressure liquid refrigerant is used as the cooling heat source. The operation of the solenoid valves 10a and 10b is such that when the solenoid valve 10a is opened (the solenoid valve 10b is closed), the capacity control pipe 15 is switched to switch the capacity of the compressor 1a.
When the solenoid valve 10b is opened (the solenoid valve 10a is closed), a low pressure may be applied to the capacity control pipe 15a. In the configuration of FIG. 28, in both the cooling operation and the heating operation, the high-pressure side refrigerant valve 10a is opened, and the high-pressure liquid refrigerant can be supplied from the pipe 43. There is no problem with the controllability of the operating capacity of the vehicle.

The high-pressure liquid refrigerant condensed in the refrigeration cycle is supplied to the solenoid valves 10a and 10b, so that the solenoid valve 1
It also functions as a cooling means for cooling Oa and 10b.
That is, the high-pressure liquid refrigerant supplied from the pipe 43 flows into the high-pressure side electromagnetic valve 10a and cools it. Solenoid valve 10a,
10b is controlled to be opened and closed alternately in a short cycle. At the timing of opening, the high-pressure side solenoid valve 10a is switched to the low-pressure side solenoid valve 10b.
b to cool it. The temperature of the high-pressure liquid refrigerant is about the condensation temperature of the refrigeration cycle, and is about 50 ° C.
Deterioration of the material of the solenoid valves 10a and 10b indicates that the temperature of the solenoid valves is 1
It is designed so that if it can be cooled down to 20 ° C., it can be prevented.
, The electromagnetic valves 10a and 10b can be sufficiently cooled.

As described above, in the present embodiment, the high-pressure liquid refrigerant is supplied to the solenoid valves 10a and 10b to cool them, thereby preventing deterioration of the materials of the solenoid valves 10a and 10b due to a rise in temperature. The life of 10a and 10b can be extended,
The reliability in the opening / closing operation can be improved.

FIG. 29 is an explanatory view showing another configuration of the refrigeration / air-conditioning apparatus according to the eighth embodiment. FIG. 29 (a) shows the configuration when the outdoor unit is viewed from the front, and FIG. Shows the configuration when the outdoor unit is viewed from the side. In this configuration, the cooling means for cooling the solenoid valves 10a and 10b is configured to be cooled by the outside air around the refrigerating air conditioner.

The outdoor unit 44 is equipped with the compressors 1a and 1b, the four-way valve 4, the outdoor heat exchanger 5 using air as a heat source, and the like. In FIG. The outdoor heat exchanger 5 is arranged in the portion. As shown by the arrow in FIG. 29B, the air sucked from the front and back surfaces exchanges heat in the outdoor heat exchanger 5, and then the air is discharged upward. The lower quarter of the outdoor unit 44 is a machine room 45, and the compressor 1a and the solenoid valve 10
a and 10b are arranged. Here, as shown in FIG. 29B, the flow of the wind of the outdoor unit 44 is partially passed through the machine room 45 to cool the solenoid valves 10a and 10b disposed in the machine room 45 with outside air. Becomes possible.
Since the temperature of the outside air is at most about 40 ° C., the temperature of the solenoid valve can be cooled to 120 ° C. or less.

Thus, the solenoid valve 10a,
10b can be sufficiently cooled to prevent deterioration of the material of each member due to a rise in temperature of the solenoid valves 10a and 10b.
It is possible to enhance the reliability in driving the a and b.

Embodiment 9 FIG. Hereinafter, a control valve according to a refrigeration / air-conditioning apparatus according to Embodiment 9 of the present invention will be described. FIG. 30 is a cross-sectional view showing a configuration of the control valve according to the present embodiment. In the figure, 46a and 46b are deceleration means, for example, springs. Other configurations are the same as those in FIG. As described above, the control valve that performs switching during the time control operation of the compressor 1a that can be operated with a stepwise capacity is required to have a large number of serviceable opening and closing times. This control valve is a movable valve 37
The opening and closing of the flow path by the movement of the flow path, the strength at the contact portion between the movable valve 37 and the valve seat 38 when the flow path is closed, and the plunger 39 and the movable valve 37 when the flow path is opened. Considering this, it is desirable to use stone or metal for the material of these contact portions. However, when stone or metal is used as the material of each contact portion, a collision sound is generated when the movable valve 37 and the valve seat 38 collide as described in the related art. In particular, when the time control operation of the compressor 1a is performed, since the electromagnetic valves 10a and 10b are opened and closed once every several seconds to several tens of seconds, a collision sound is generated once every several seconds to several tens of seconds. Therefore, if the collision sound is loud, the sound is continuously generated in the outdoor unit 44 as noise, which is a problem for the surrounding environment. Therefore, it is necessary to increase the reliability of the solenoid valves 10a and 10b and to reduce the generated driving noise.

In this embodiment, as the shock absorbing means,
Teflon, which is one of resins, is used as a material of a portion that contacts when the solenoid valves 10a and 10b are closed, for example, a portion of the portion where the movable valve 37 and the valve seat 38 contact each other. Teflon is softer than stone or metal and has a certain strength against impact, so it absorbs the impact force at the time of collision between the movable valve 37 and the valve seat 38, and produces a lower collision sound than when using stone or metal. It becomes possible to reduce. Similarly, the solenoid valves 10a, 1
It is also necessary to reduce a collision sound when the movable valve 37 collides with the plunger 39, for example, a portion that contacts when the valve 0b is opened, for example, the movable valve 37 is sucked by the plunger 39. For this reason, for example, Teflon is also used for the portion where the movable valve 37 and the plunger 39 are in contact with each other, thereby reducing the collision noise.

As another shock absorbing means, the moving speed of the movable valve can be reduced to reduce the shock caused by the opening and closing of the control valve. As shown in FIG. 30, springs 46a and 46b, which are elastic bodies, are arranged above and below the movable valve 37. One end of the spring 46a is connected to the valve seat 38 and the other end is a movable valve 37.
It is connected to the. When the flow path is closed by the spring 46a, the speed at which the movable valve 37 moves downward and hits the valve seat 38 can be reduced, so that the collision between the movable valve 37 and the valve seat 38 can be softened. Therefore, the movable valve 37 and the valve seat 3
8, the reliability of the opening / closing operation of the solenoid valves 10a and 10b can be improved, and the occurrence of collision noise can be reduced. One end of a spring 46b disposed on the upper side is connected to the plunger 39, and the other end is connected to the movable valve 37. The spring 46b can reduce the speed at which the movable valve 37 moves upward and hits the plunger 39 when the flow path is opened, so that when a collision occurs, the speed of the collision can be reduced by the spring 46 disposed above. So
The collision between the movable valve 37 and the plunger 39 is softened. Therefore, the wear of the movable valve 37 and the plunger 39 can be suppressed, the reliability of the opening and closing operation of the solenoid valves 10a and 10b can be improved, and the occurrence of collision noise can be reduced. The ends connected to the fixed sides of the springs 46a and 46b are not limited to the above-described configuration, and may be connected anywhere on the fixed side in the control valve.

Embodiment 10 FIG. Hereinafter, a refrigeration / air-conditioning apparatus according to Embodiment 10 of the present invention will be described, for example, an apparatus for performing indoor air conditioning. FIG. 31 is a refrigerant circuit diagram illustrating a configuration of a refrigeration / air-conditioning apparatus according to the present embodiment. In the figure, 47a is a pressure measuring means for measuring the high pressure of the refrigeration cycle, here a pressure sensor, 47b is a pressure measuring means for measuring the low pressure of the refrigeration cycle, here a pressure sensor, 48
Reference numerals a and 48b denote temperature measuring means for measuring the outlet temperature of the indoor heat exchangers 8a and 8b during the cooling operation.
Reference numerals 48c and 48d denote temperature measuring means for measuring the outlet temperatures of the indoor heat exchangers 8a and 8b during the heating operation, which are temperature sensors in this case. The other configuration in FIG. 31, the flow of the refrigerant, and the method of switching the capacity of the compressor in FIG. 31 are the same as those in the first embodiment.

In the present embodiment, high-pressure, low-pressure, indoor heat exchangers 8a, 8
The outlet temperature of b is measured by the pressure sensors 47a, 47b and the temperature sensors 48a, 48b, 48c, 48d. Based on the measured operation information, the control means (not shown) controls the operation capacity of the compressors 1a and 1b and controls the opening of the expansion valves 7a and 7b. The control of the operating capacity of the compressors 1a and 1b by the control means is the same as the method described in the first embodiment. In the compressor 1a, the compressor 1a is controlled by different stages at each time to which a short-cycle time distribution is allocated. , And the time distribution is changed to change the average capacity in a short cycle.
The operating capacity is continuously changed as a whole by combining the stops. The degree of opening of the expansion valves 7a and 7b is low during cooling operation (measured by the pressure sensor 47b), and the outlet temperature of the indoor heat exchangers 8a and 8b during cooling operation (temperature sensor 48).
a, 48b), the degree of superheat at the outlet of the indoor heat exchanger is determined, and control is performed so that the degree of superheat becomes a preset target value. During heating operation, high pressure (pressure sensor 4
7a), and the indoor heat exchanger 8a in the heating operation,
Based on the outlet temperature 8b (measured by the temperature sensors 48c and 48d), the degree of supercooling at the outlet of the indoor heat exchanger is obtained, and control is performed so that the degree of supercooling becomes a preset target value.

The problem with this embodiment is that the measured driving information tends to vary. That is, in the compressor 1a that can be operated with a stepwise capacity, when the capacity is switched in a short cycle by performing the time control operation, the information of the measured pressure and temperature fluctuates. If control is performed based on the above, stable control cannot be performed.
FIG. 32 is an explanatory diagram showing a method for measuring operation information, for example, pressure, in which the horizontal axis indicates time, and the vertical axis indicates the operation capacity of the compressor and the accompanying pressure. When the compressor 1a is performing a time control operation in which, for example, two stages of a maximum capacity and a minimum capacity are switched in a short cycle, when the compressor operation capacity changes from the minimum capacity to the maximum capacity, the high pressure becomes high and the low pressure becomes low, Conversely, when the compressor operating capacity changes from the maximum capacity to the minimum capacity,
High pressures are low and low pressures are high.

Therefore, in this embodiment, the pressure and temperature are measured at the timing indicated by the dotted line in FIG. For example, the time when the operating capacity of the compressor 1a switches, that is, the pressure and the temperature are measured for a predetermined time interval at a fixed time interval shorter than the short cycle time, and an average value of a plurality of measurement values measured in the time period is obtained. Operation control is performed based on the average value.
The average value of the obtained operation information has no influence due to the fluctuation caused by the time control operation of the compressor 1a and is reduced to a negligible level, so that stable operation control can be performed based on this operation information. Here, the predetermined period to be measured is equal to or longer than the length of the short cycle.

In addition to performing the operation control by obtaining the average value of the plurality of pieces of operation information measured as described above,
The control may be performed based on the maximum value of the plurality of measurement values measured during the predetermined period, or the minimum value of the plurality of measurement values measured during the predetermined period may be determined. The control may be performed as follows. Alternatively, a plurality of measured values may be arranged in order from large to small or from small to large, and may be ranked, and control may be performed based on measured values in a certain fixed order. In any case, by performing control based on a plurality of operation information measured in a period of a short cycle or more, measurement can be performed without fluctuation of operation information such as pressure and temperature, and stable operation control is performed. be able to.

Next, another method of measuring the operation information relating to the refrigeration / air-conditioning apparatus according to the present embodiment will be described. FIG.
The pressure and temperature are measured at the timing indicated by the dotted line in FIG. That is, the pressure and temperature are measured at approximately the intermediate timing between the time when the operating capacity of the compressor 1a is stepwise switched from the minimum capacity to the maximum capacity and the time when the operating capacity is stepwise switched from the maximum capacity to the minimum capacity. Is also good. By measuring at such a timing, pressure and temperature information can be measured without being affected by fluctuations. Further, when the measurement is performed at an intermediate timing within a short period, even if a pressure fluctuation occurs, a value that is substantially an average value of the fluctuated pressure can be measured, so that an average state of the refrigeration cycle can be grasped.

Further, the timing for performing the measurement is not limited to about the middle between the time when the operating capacity of the compressor switches from the minimum capacity to the maximum capacity and the time when the operating capacity switches from the maximum capacity to the minimum capacity. It may be performed at a certain timing between the time when the minimum capacity is switched to the maximum capacity and the time when the maximum capacity is switched to the minimum capacity. Also, even if the measurement is performed at a certain timing between the time when the operating capacity of the compressor switches from the maximum capacity to the minimum capacity and the time when the compressor capacity switches from the minimum capacity to the maximum capacity, the operating information is similarly changed without fluctuation. Can be measured.
That is, if measurement is performed at a predetermined time within a short cycle, operation information that is not affected by fluctuations is obtained. By performing operation control based on this information, stable control can be performed. The predetermined time in this short cycle may be set in advance by confirming that measurement can be stably performed by an experiment or the like. In addition, even if it is not always measured at a predetermined time in the short cycle range, the characteristics of the fluctuation, for example, the fluctuation width in which the measurement value fluctuates in the short cycle time and the range can be grasped in advance by experiments or the like, As long as the measured value can be corrected, it is not necessary to always measure at a predetermined time within a short cycle range, and there is no restriction on the measurement timing.

In the third to tenth embodiments, the refrigerating and air-conditioning apparatus having the compressor 1b having a fixed capacity in addition to the compressor 1a which can be operated with a stepped capacity has been described. It is not necessary to have a configuration having the compressor 1b, and it may be a configuration having a plurality of compressors 1b of a fixed capacity, or a plurality of compressors that can be operated with a stepwise capacity as in the first embodiment. The configuration having the same effects as those of the embodiments. The refrigeration / air-conditioning apparatus may be configured to have one compressor that can be operated at least in a stepwise capacity. In particular, by providing a plurality of compressors, the operation patterns can be variously combined, so that the combination range of the operation capacity is widened. Further, by providing a plurality of compressors that can be operated with stepwise capacities, the capacity fluctuation width can be reduced, which is more effective.

Further, in the first to tenth embodiments, the case where two indoor heat exchangers are combined has been described. However, the number of indoor heat exchangers may be one or three or more. The same effect can be obtained.

The refrigerants used in the refrigeration and air-conditioning systems according to Embodiments 1 to 10 are not limited to R22, which is currently frequently used in refrigeration and air-conditioning systems, but also R13.
Similar effects can be obtained by using HFC-based refrigerants such as 4a and R32, R407C, R410A and R404A which are mixed refrigerants of HFC-based refrigerants, natural refrigerants such as ammonia, propane and butane, and mixed refrigerants of these refrigerants. be able to.

[0153]

As described above, according to the refrigeration / air-conditioning apparatus according to the first aspect of the present invention, at least one compressor operable with a stepwise capacity and a stepwise separate compressor are provided. A compressor operable with a capacity or at least one compressor operable with a fixed capacity is provided, and the compressor operable with the gradual capacity is provided with a capacity of different stages at each time to which a short cycle time distribution is distributed. By changing the time distribution, changing the average capacity in the short cycle, and continuously changing the total operating capacity of the plurality of compressors, adverse effects of harmonics caused by using an inverter To reduce fluctuations in compressor operating capacity, thereby suppressing fluctuations in the refrigeration cycle, such as pressure fluctuations, and reducing fluctuations in refrigeration capacity and air conditioning capacity, such as fluctuations in blown air temperature. When operating the device There is an effect that aptitude can be ensured.

Further, according to the refrigeration / air-conditioning apparatus according to claim 2 of the present invention, in claim 1, the operating capacity of the plurality of compressors is reduced to at least two compressors which can be operated with stepwise capacity. In the case of shared operation, the operating capacity shared by the compressor operable at the stepwise capacity is avoided by sharing the stepwise capacity of the compressor while avoiding that the capacity matches the minimum capacity. , The fluctuation range on the refrigeration cycle, such as pressure fluctuation due to fluctuations in the operating capacity of the compressor,
It has the effect of reducing fluctuations in refrigeration capacity and air-conditioning capacity, such as fluctuations in blow-out air temperature, ensuring comfort during operation of the refrigeration and air-conditioning system and stabilizing operation by equalizing the discharge temperature of the operating compressor. .

According to the refrigeration / air-conditioning apparatus of the third aspect of the present invention, in the first or second aspect, each of the at least two compressors which can be operated in a stepwise capacity has a short cycle time. When operating at different stages of capacity at each time when the distribution is distributed, the temporal variation in the short cycle of the total of the operating capacity of each compressor is large for each of the compressors operating in the short cycle. By operating the compressor in combination with the short-cycle time distribution of each of the compressors and the operating capacity of each time so that the difference is smaller than the difference between the total of the operating capacity of the one compressor and the total of the operating capacity of the smaller one, In order to reduce fluctuations in the refrigeration cycle, such as pressure fluctuations, by reducing fluctuations in the operating capacity of the air conditioner, and to reduce fluctuations in refrigeration capacity and air conditioning capacity, such as fluctuations in blown air temperature, In comfort There is Ruiu effect.

Further, according to the refrigeration / air-conditioning apparatus according to claim 4 of the present invention, in claim 3, two compressors operable with a stepwise capacity are provided, and one of the compressors in a short cycle is provided. At least part of the time during which the larger capacity operation of the stage is performed, the other compressor performs the smaller capacity operation of the stage, and the other compressor performs the operation of the larger capacity of the stage. At least a part of the time when the capacity operation is performed, one of the compressors is operated at the smaller capacity of the stage, thereby reducing the fluctuation of the operation capacity of the compressor. This has the effect of suppressing fluctuations in the refrigeration cycle, such as pressure fluctuations, reducing fluctuations in refrigeration capacity and air conditioning capacity, such as fluctuations in the temperature of blown air, and ensuring comfort during operation of the refrigeration and air conditioning system.

Further, according to the refrigeration / air-conditioning apparatus according to claim 5 of the present invention, the compressor which can be operated with a stepwise capacity, the first
A heat exchanger, a throttle means, a refrigeration cycle in which a refrigerant is circulated through the second heat exchanger, and the compressor is operated at different stages of capacity at each time when a short-cycle time distribution is allocated, and the time distribution is determined. And a capacity control means for changing the average capacity in the short cycle by changing the internal capacity on the high pressure side of the refrigeration cycle so as to reduce the high pressure side pressure fluctuation width. With the above, or by setting the internal volume on the low pressure side of the refrigeration cycle to a second predetermined volume or more that reduces the low pressure side pressure fluctuation width, the refrigeration cycle is subjected to pressure fluctuations due to fluctuations in operating capacity. There is an effect that the fluctuation width is suppressed, the fluctuation of the refrigeration capacity and the air conditioning capacity such as the fluctuation of the outlet air temperature is reduced, and the comfort during the operation of the refrigeration and air conditioning apparatus can be secured.

According to the refrigeration and air-conditioning apparatus of claim 6 of the present invention, in claim 5, the first predetermined volume or the second predetermined volume is a high pressure side generated in the refrigeration cycle by operation of the compressor. Or the allowable value of the pressure fluctuation width on the low pressure side, the length of the short cycle, and the operating capacity fluctuation width of the compressor in the short cycle, by determining based on the high pressure side or the low pressure side volume, It can be set to satisfy operating conditions, equipment configuration and comfort when using the equipment, suppresses fluctuations in the refrigeration cycle such as pressure fluctuations due to fluctuations in the operating capacity of the compressor, and fluctuations in blown air temperature For example, there is an effect that fluctuations in refrigeration capacity and air conditioning capacity can be reduced, and comfort during operation of the refrigeration and air conditioning apparatus can be secured.

Further, according to the refrigeration / air-conditioning apparatus of the present invention, the compressor which can be operated with the stepwise capacity,
A heat exchanger, a throttle means, a refrigeration cycle in which a refrigerant is circulated through the second heat exchanger, and the compressor is operated at different stages of capacity at each time when a short-cycle time distribution is allocated, and the time distribution is determined. A refrigerating and air-conditioning system having a capacity control means for changing the average capacity in the short cycle by changing the amount of air generated on the high-pressure side or low-pressure side of the refrigerating cycle. By providing a refrigerant container that reduces pressure fluctuations on the high-pressure side or low-pressure side, fluctuations in the refrigeration cycle, such as pressure fluctuations due to fluctuations in the operating capacity of the compressor, are suppressed, and refrigeration capacity, such as fluctuations in blown air temperature. In addition, there is an effect that fluctuations in air conditioning capacity can be reduced and comfort during operation of the refrigeration air conditioner can be secured.

According to the refrigeration / air-conditioning apparatus of the present invention, the liquid receiver provided at the outlet of the heat exchanger operating as an oil separator or a condenser is provided as the refrigerant container provided on the high pressure side. In this way, the range of fluctuations in the refrigeration cycle, such as pressure fluctuations due to fluctuations in the operating capacity of the compressor, is suppressed, and fluctuations in refrigeration capacity and air conditioning capacity, such as fluctuations in blown air temperature, are reduced. In this case, there is an effect that the comfort during the operation can be secured and the reliability of the compressor operation can be improved.

According to the refrigeration / air-conditioning apparatus of the ninth aspect of the present invention, the accumulator provided on the suction side of the compressor is used as the refrigerant container provided on the low pressure side in the seventh aspect. In addition to suppressing fluctuations in the refrigeration cycle such as pressure fluctuations due to fluctuations in operating capacity, minimizing fluctuations in refrigeration capacity and air conditioning capacity, such as fluctuations in blown air temperature, and ensuring comfort during refrigeration and air conditioning system operation. In addition, there is an effect that the liquid compression operation in the compressor can be prevented and the reliability of the compressor operation can be improved.

Further, according to the refrigeration / air-conditioning apparatus of the tenth aspect of the present invention, the refrigerant is circulated through the compressor, the first heat exchanger, the throttling means, and the second heat exchanger which can be operated with a stepwise capacity. A refrigeration cycle, and a capacity control unit that operates the compressor at different stages of capacity at each time when the short cycle time distribution is distributed, and changes the time distribution to change the average capacity in the short cycle. In the refrigeration air conditioner provided with, a high-pressure side or a low-pressure side constituting the refrigeration cycle is provided with a resistance element for adding a flow resistance when the refrigerant flows, the high-pressure side generated in the refrigeration cycle by operation of the compressor Alternatively, by reducing pressure fluctuations on the low pressure side, fluctuations in the refrigeration cycle, such as pressure fluctuations due to fluctuations in the operating capacity of the compressor, are suppressed, and fluctuations in refrigeration capacity and air conditioning capacity, such as fluctuations in blown air temperature, are reduced. Comb, there is an effect that the comfort of the time of the refrigerating and air-conditioning apparatus operation can be secured.

According to the refrigeration / air-conditioning apparatus of claim 11 of the present invention, the resistance element provided on the high pressure side in claim 10 is a check valve provided on the discharge side of the compressor. The fluctuation range of the refrigeration cycle such as the pressure fluctuation due to the fluctuation of the operating capacity of the refrigeration cycle is suppressed, the fluctuation of the refrigeration capacity and the air conditioning capacity such as the fluctuation of the outlet air temperature is reduced, and the comfort during the operation of the refrigeration and air conditioning system can be secured At the same time, there is an effect that the liquid compression operation at the time of start-up by the compressor can be prevented and the reliability of the compressor operation can be improved.

According to the refrigeration / air-conditioning apparatus of the twelfth aspect of the present invention, the refrigerant circulates through the compressor, the first heat exchanger, the throttling means, and the second heat exchanger which can be operated in a stepwise capacity. A refrigeration cycle, and a capacity control unit that operates the compressor at different stages of capacity at each time when the short cycle time distribution is distributed, and changes the time distribution to change the average capacity in the short cycle. In the refrigeration air conditioner provided with, by providing a bypass circuit that bypasses the high pressure side and the low pressure side of the refrigeration cycle, by reducing the pressure fluctuation on the high pressure side or the low pressure side generated in the refrigeration cycle by operation of the compressor In addition, the fluctuation range of the refrigeration cycle, such as pressure fluctuations due to the fluctuations in the operating capacity of the compressor, is suppressed, and fluctuations in the refrigeration capacity and air conditioning capacity, such as fluctuations in the outlet air temperature, are reduced. There is an effect that sex can be ensured.

According to the refrigeration / air-conditioning apparatus of claim 13 of the present invention, the bypass circuit of claim 12
By using a circuit that connects the discharge side and the suction side of the compressor, fluctuations in the refrigeration cycle, such as pressure fluctuations due to fluctuations in the operating capacity of the compressor, are suppressed, and refrigeration capacity, This has the effect of reducing fluctuations in the air conditioning capacity and ensuring comfort during operation of the refrigeration air conditioner.

According to the refrigeration / air-conditioning apparatus of claim 14 of the present invention, in claim 12 or claim 13, a control valve is provided in the bypass circuit, and the compressor operable with a stepwise capacity can be shortened. When operating at different stages of capacity at each time of allocating the time distribution of the cycle, the control valve opens the bypass circuit, and when the compressor operates at a fixed capacity, the control valve opens the bypass circuit. By closing it, the energy efficiency of the refrigeration cycle is maintained, fluctuations in the refrigeration cycle such as pressure fluctuations due to fluctuations in the operating capacity of the compressor are suppressed, and refrigeration capacity and air conditioning capacity such as fluctuations in the temperature of the blown air. Of the air conditioner can be reduced, and the comfort during operation of the refrigeration and air conditioning system can be ensured.

According to a refrigeration / air-conditioning apparatus according to claim 15 of the present invention, the bypass circuit in claim 12 is
A circuit that returns the high-pressure liquid refrigerant condensed by the heat exchanger that operates as a condenser of the refrigeration cycle to the compressor suction side allows for fluctuations in the refrigeration cycle such as pressure fluctuations due to fluctuations in the operating capacity of the compressor. Compressor operation by reducing fluctuations in refrigeration capacity and air-conditioning capacity, such as fluctuations in blow-out air temperature, ensuring comfort during refrigeration and air-conditioning system operation and preventing excessive rise in discharge temperature of the compressor There is an effect that the reliability of the device can be improved.

According to the refrigeration / air-conditioning apparatus of claim 16 of the present invention, in claim 15, a pressure reducing means for reducing the pressure of the high-pressure liquid refrigerant is provided in the bypass circuit.
By providing a heat exchanger that exchanges heat between the refrigerant depressurized by the decompression means and the high-pressure liquid refrigerant condensed by the condenser, fluctuations in the refrigeration cycle such as pressure fluctuations due to fluctuations in the operating capacity of the compressor The width of the compressor is reduced, the fluctuations in refrigeration capacity and air-conditioning capacity, such as fluctuations in the temperature of the blown air, are reduced, ensuring comfort during operation of the refrigeration and air-conditioning system, and preventing the compressor discharge temperature from rising excessively. There is an effect that the operation efficiency of the refrigeration air conditioner can be improved by improving the reliability of the operation and reducing the pressure loss in the gas pipe while eliminating the performance loss of the refrigeration air conditioner due to the bypass.

Further, according to the refrigeration / air-conditioning apparatus of claim 17 of the present invention, the bypass circuit in claim 12 is a circuit for returning the oil separated by the oil separator to the low pressure side, thereby reducing the operating capacity of the compressor. In addition to suppressing fluctuations in the refrigeration cycle, such as pressure fluctuations due to fluctuations, reducing fluctuations in refrigeration capacity and air conditioning capacity, such as fluctuations in the temperature of the blown air, it is possible to ensure comfort during operation of the refrigeration and air conditioning system, This prevents the oil from being depleted, thereby improving the reliability of the compressor operation.

Further, according to the refrigeration / air-conditioning apparatus of the eighteenth aspect of the present invention, the refrigerant is circulated through the compressor, the first heat exchanger, the throttling means, and the second heat exchanger which can be operated in a stepwise capacity. A refrigeration cycle, and a capacity control unit that operates the compressor at different stages of capacity at each time when the short cycle time distribution is distributed, and changes the time distribution to change the average capacity in the short cycle. In a refrigeration / air-conditioning apparatus provided with a control valve for switching the operating capacity of the compressor in the short-period time distribution, an oil supply unit for supplying oil to the control valve is provided. There is an effect that wear of the contact portion can be prevented, the life of the control valve can be prolonged, and the reliability of the refrigeration / air-conditioning apparatus can be improved.

According to a refrigeration / air-conditioning apparatus according to claim 19 of the present invention, in claim 18, an oil separator is provided on the discharge side of the compressor, and oil supply means is connected to the oil or oil separated by the oil separator. By using an oil supply circuit that supplies the refrigerant gas after oil separation to the control valve,
The oil separated by the oil separator or the oil mixed with the refrigerant gas after oil separation prevents wear of the contact part when opening and closing the control valve, prolongs the life of the control valve, and improves the reliability of the refrigeration and air conditioning system. There is an effect that it can be improved.

Further, according to the refrigeration / air-conditioning apparatus of claim 20 of the present invention, the oil supply means of claim 18 is an oil supply circuit for supplying gas refrigerant discharged from the compressor to the control valve. In addition, the oil of the compressor discharged together with the gas refrigerant prevents wear of the contact portion when the control valve is opened and closed, has the effect of prolonging the life of the control valve, and improving the reliability of the refrigeration and air conditioning system.

Further, according to the refrigeration / air-conditioning apparatus of the present invention, the refrigerant is circulated through the compressor, the first heat exchanger, the throttling means, and the second heat exchanger which can be operated with a stepwise capacity. A refrigeration cycle, and a capacity control unit that operates the compressor at different stages of capacity at each time when the short cycle time distribution is distributed, and changes the time distribution to change the average capacity in the short cycle. In a refrigeration / air-conditioning system including a control valve for switching the operating capacity of the compressor in the short-period time distribution, a cooling means for cooling the control valve is provided, so that the temperature of the control valve for controlling the operating capacity increases. And the reliability of control valve drive can be ensured.

Further, according to the refrigeration / air-conditioning apparatus of claim 22 of the present invention, the cooling means of claim 21 uses the high-pressure liquid refrigerant condensed by the heat exchanger operating as the condenser of the refrigeration cycle as the control valve. With the supply of the refrigerant circuit, an increase in the temperature of the control valve for controlling the operation capacity can be reduced by using the refrigerant, and there is an effect that the reliability of the control valve drive can be ensured.

Further, according to the refrigeration / air-conditioning apparatus of claim 23 of the present invention, the cooling means in claim 21 is configured to cool the control valve by the outside air around the refrigeration / air-conditioning apparatus, thereby reducing the operating capacity. There is an effect that the temperature rise of the control valve to be controlled can be reduced by using outside air, and the reliability of control valve driving can be ensured.

Further, according to the refrigeration / air-conditioning apparatus according to claim 24 of the present invention, the refrigerant is circulated through the compressor, the first heat exchanger, the throttling means, and the second heat exchanger which can be operated with a stepwise capacity. A refrigeration cycle, and a capacity control unit that operates the compressor at different stages of capacity at each time when the short cycle time distribution is distributed, and changes the time distribution to change the average capacity in the short cycle. A refrigeration / air-conditioning system including a control valve for switching the operating capacity of the compressor in the short-period time distribution by opening and closing a flow path by moving a movable valve, wherein the control valve contacts the control valve by moving the movable valve. Providing the movable valve that hits the contacting portion or the contacting portion with the impact mitigation means for alleviating the impact thereof has an effect that the driving sound at the time of driving the control valve can be reduced and the noise can be reduced.

According to the refrigeration / air-conditioning apparatus of claim 25 of the present invention, the shock absorbing means of claim 24 is
At least a portion of the material of the movable valve that is in contact with the movable valve or the contact portion by the movement of the movable valve is made of resin to reduce the impact, thereby reducing driving noise when driving the control valve. There is an effect that noise can be reduced.

Further, according to the refrigeration / air-conditioning apparatus according to claim 26 of the present invention, the shock absorbing means according to claim 24 is provided with deceleration means for decelerating the movement of the movable valve. By reducing the speed of the control valve to reduce the impact, it is possible to reduce the driving noise when driving the control valve, reduce the noise, and prolong the life of the control valve. There is an effect that it can be obtained.

Further, according to the refrigeration / air-conditioning apparatus of the twenty-seventh aspect of the present invention, the refrigerant is circulated through the compressor, the first heat exchanger, the throttling means, and the second heat exchanger which can be operated in stepwise capacity. A refrigeration cycle, and a capacity control unit that operates the compressor at different stages of capacity at each time when the short cycle time distribution is distributed, and changes the time distribution to change the average capacity in the short cycle. Measuring means for measuring the operation information of the refrigeration cycle during operation a plurality of times within a predetermined time having a length equal to or longer than the short cycle, and the capacity control means based on the obtained plurality of operation information. By performing the control of the refrigeration cycle including the control in the above, there is an effect that the control corresponding to the changed operation information is performed, and the operation of the refrigeration air conditioner can be stably controlled.

Further, according to the refrigeration / air-conditioning apparatus of the twenty-eighth aspect of the present invention, the refrigerant is circulated through the compressor, the first heat exchanger, the throttling means, and the second heat exchanger which can be operated in a stepwise capacity. A refrigerating cycle, capacity control means for operating the compressor with different capacities at each time of allocating a short cycle time distribution, and changing the time distribution to change the average capacity in the short cycle. Measuring means for measuring the operation information of the refrigeration cycle during a predetermined time within the short cycle,
By controlling the refrigeration cycle including the control by the capacity control means based on the obtained operation information, control corresponding to the fluctuated operation information is performed, and the operation control of the refrigeration / air-conditioning apparatus is stably performed. There is an effect that can be.

According to a refrigeration / air-conditioning apparatus according to claim 29 of the present invention, in any one of claims 5 to 28, the refrigeration cycle is operated with a stepwise capacity separately from the compressor. By providing at least one possible compressor or a compressor operating at a fixed capacity, in addition to the effect of any one of claims 1 to 28, the fluctuation of the operating capacity of the compressor can be reduced. Therefore, there is an effect that comfort during operation of the refrigeration / air-conditioning apparatus can be ensured.

[Brief description of the drawings]

FIG. 1 is a refrigerant circuit diagram showing a configuration of a refrigeration / air-conditioning apparatus according to Embodiment 1 of the present invention.

FIG. 2 is a sectional view showing a compression chamber of the scroll compressor according to the first embodiment.

FIG. 3 is a plan view showing a compression chamber of the scroll compressor according to the first embodiment.

FIG. 4 is an explanatory diagram showing a state of temporal opening / closing control of the electromagnetic valve according to the first embodiment.

FIG. 5 is a graph showing a change in operating capacity of each compressor according to the first embodiment, and showing a compressor operating capacity [HP] with respect to a required operating capacity [HP].

FIG. 6 is a refrigerant circuit diagram showing a configuration of a refrigeration / air-conditioning apparatus according to Embodiment 2 of the present invention.

FIG. 7 is a graph showing an example of a change in operating capacity of each compressor according to the second embodiment, and showing a compressor operating capacity [HP] with respect to a required operating capacity [HP].

FIG. 8 is a graph showing another example of a change in the operating capacity of each compressor according to the second embodiment, and showing a compressor operating capacity [HP] with respect to a required operating capacity [HP].

FIG. 9 is a graph showing still another example of a change in the operating capacity of each compressor according to the second embodiment, and showing a compressor operating capacity [HP] with respect to a required operating capacity [HP].

FIG. 10 is an explanatory diagram showing a change over time of the operating capacity of each compressor according to the second embodiment.

FIG. 11 is an explanatory diagram showing a time change of the operating capacity of each compressor according to the second embodiment.

FIG. 12 is an explanatory diagram showing a change over time of the operating capacity of each compressor according to the second embodiment.

FIG. 13 is a refrigerant circuit diagram illustrating a configuration of a refrigeration / air-conditioning apparatus according to Embodiment 3 of the present invention.

FIG. 14 is a graph showing {volume (L) of equipment and piping constituting the high pressure side} / operating capacity fluctuation width [HP] with respect to the operating capacity control interval according to the third embodiment.

FIG. 15 is a graph showing {volume (L) of equipment and piping constituting the low pressure side} / operating capacity fluctuation width [HP] with respect to the operating capacity control interval according to the third embodiment.

FIG. 16 is a refrigerant circuit diagram showing a configuration of a refrigeration / air-conditioning apparatus according to Embodiment 4 of the present invention.

FIG. 17 is a refrigerant circuit diagram showing another configuration of the refrigeration and air-conditioning apparatus according to Embodiment 4.

FIG. 18 is a refrigerant circuit diagram showing still another configuration of the refrigeration / air-conditioning apparatus according to Embodiment 4.

FIG. 19 is a refrigerant circuit diagram showing a configuration of a refrigeration / air-conditioning apparatus according to Embodiment 5 of the present invention.

FIG. 20 is a refrigerant circuit diagram showing another configuration of the refrigeration and air-conditioning apparatus according to Embodiment 5.

FIG. 21 is a refrigerant circuit diagram illustrating a configuration of a refrigeration and air-conditioning apparatus according to Embodiment 6 of the present invention.

FIG. 22 is a refrigerant circuit diagram showing another configuration of the refrigeration and air-conditioning apparatus according to Embodiment 6.

FIG. 23 is a refrigerant circuit diagram showing still another configuration of the refrigeration / air-conditioning apparatus according to Embodiment 6.

FIG. 24 is a refrigerant circuit diagram showing a configuration of a refrigeration / air-conditioning apparatus according to Embodiment 7 of the present invention.

FIG. 25 is a sectional view showing a structure of a control valve according to a seventh embodiment.

FIG. 26 is a refrigerant circuit diagram showing another configuration of the refrigeration and air-conditioning apparatus according to Embodiment 7.

FIG. 27 is a refrigerant circuit diagram showing still another configuration of the refrigeration / air-conditioning apparatus according to Embodiment 7.

FIG. 28 is a refrigerant circuit diagram illustrating a configuration of a refrigeration / air-conditioning apparatus according to Embodiment 8 of the present invention.

FIG. 29 is an explanatory diagram showing another configuration of the refrigeration and air-conditioning apparatus according to the eighth embodiment, where FIG. 29 (a) shows the configuration when the outdoor unit is viewed from the front, and FIG. 29 (b) shows the outdoor unit. Is shown when viewed from the side.

FIG. 30 is a sectional view showing a control valve according to a refrigeration / air-conditioning apparatus according to Embodiment 9 of the present invention.

FIG. 31 is a refrigerant circuit diagram illustrating a configuration of a refrigeration and air-conditioning apparatus according to Embodiment 10 of the present invention.

FIG. 32 is an explanatory diagram showing a method for measuring operation information of a refrigeration / air-conditioning apparatus according to Embodiment 10.

FIG. 33 is an explanatory diagram showing another method for measuring the operation information of the refrigeration / air-conditioning apparatus according to the tenth embodiment.

FIG. 34 is a refrigerant circuit diagram showing a conventional air conditioner.

FIG. 35 is an explanatory diagram showing a state of temporal opening / closing control of a solenoid valve in a conventional air conditioner.

[Description of Signs] 1a, 1c Compressor operable with stepwise capacity, 1b
Constant capacity compressor, 2a, 2b Discharge piping, 3a, 3b
Suction pipe, 4 refrigerant flow switching means, 5 first heat exchanger, 6 liquid pipe, 7 throttle means, 8a, 8b 2nd heat exchanger, 9 gas pipe, 10a, 10b control valve, 16 high pressure side refrigerant container , 17 Low pressure side refrigerant container, 18 oil separator, 19 oil return circuit, 30 liquid receiver, 31
Accumulator, 32, 33 resistance element, 34 bypass circuit, 35 control valve, 36 heat exchange part, 37 movable valve, 38 valve seat, 39 plunger, 40 coil,
41 valve inlet side flow path, 42 valve outlet side flow path, 43 cooling means, 44 outdoor unit, 45 machine room, 46a, 46b
Deceleration means, 47a, 47b pressure measurement means, 48a, 4
8b, 48c, 48d Temperature measuring means.

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat ゛ (Reference) F25B 1/04 F25B 1/04 Y 5/00 301 5/00 301B 13/00 104 13/00 104 43 / 02 43/02 A // F04C 18/02 311 F04C 18/02 311X (72) Inventor Osamu Morimoto 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Within Mitsubishi Electric Corporation (72) Inventor Yoshihiro Sumida Tokyo 2-3-2 Marunouchi, Chiyoda-ku, Mitsubishi Electric Corporation (72) Inventor Hiroyu Shiba 2-3-2, Marunouchi, Chiyoda-ku, Tokyo F-term in Mitsubishi Electric Corporation 3H029 AA02 AB03 AB08 BB22 BB35 BB52 CC63 CC87 CC91 3H039 AA14 BB01 BB22 CC04 CC40 3H045 AA16 AA27 BA19 BA28 BA36 BA38 CA02 CA03 CA24 CA28 CA29 DA33 DA36 DA47 EA38 3L092 GA05 GA06 GA09 HA10 HA11 JA01 JA03 JA11 KA02 K A16 LA03 LA04 LA07

Claims (29)

[Claims] At least one compressor operable at a stepwise capacity and at least one compressor operable at a stepwise capacity separately from the compressor or at a fixed capacity. The compressor, which can be operated with the stepwise capacity, is operated at a different stage capacity at each time to which the short cycle time distribution is allocated, and the time capacity is changed to change the average capacity in the short cycle. A refrigeration / air-conditioning system wherein the total operating capacity of the plurality of compressors is continuously variable. 2. The compressor according to claim 1, wherein when the operating capacity of the plurality of compressors is shared by at least two compressors that can be operated with a stepped capacity, the compressor is operated at the stepped capacity. A refrigerating and air-conditioning apparatus characterized in that the operating capacity shared by a compressor is prevented from being equal to the minimum capacity among the stepwise capacities of the compressor. 3. The compressor according to claim 1, wherein at least two compressors that can be operated with stepwise capacities are operated with capacities of different stages at respective times to which a short cycle time distribution is allocated. The time variation of the total operating capacity of each compressor within the short cycle is the sum of the larger operating capacity and the smaller operating capacity of each compressor operating in the short cycle. A refrigerating and air-conditioning system characterized in that the compressor is operated in combination with a short-cycle time distribution of each of the compressors and an operation capacity at each of the times so as to be smaller than a difference between the compressors. 4. The compressor according to claim 3, further comprising: two compressors that can be operated at stepwise capacities, wherein at least one of the compressors in a short cycle operates the larger capacity at that step. At least some of the time when the other compressor performs the smaller capacity operation of the stage while the other compressor performs the smaller capacity operation during the stage, Wherein the compressor operates at a smaller capacity at that stage. 5. A compressor operable with a stepwise capacity, the first
A heat exchanger, a throttle means, a refrigeration cycle in which a refrigerant is circulated through the second heat exchanger, and the compressor is operated at different stages of capacity at each time when a short-cycle time distribution is allocated, and the time distribution is determined. And a capacity control means for changing the average capacity in the short cycle by changing the internal capacity on the high pressure side of the refrigeration cycle so as to reduce the high pressure side pressure fluctuation width. The refrigerating air conditioner according to claim 1, wherein the internal volume on the low pressure side of the refrigeration cycle is equal to or larger than a second predetermined volume so as to reduce the low pressure side pressure fluctuation width. 6. The system according to claim 5, wherein the first predetermined volume or the second predetermined volume is an allowable value of a pressure fluctuation range on a high pressure side or a low pressure side generated in a refrigeration cycle by operation of the compressor, and a short cycle. A refrigeration / air-conditioning apparatus characterized in that it is determined based on a length and a fluctuation width of an operating capacity of the compressor in the short cycle. 7. A compressor operable with a stepwise capacity, the first
A heat exchanger, a throttle means, a refrigeration cycle in which a refrigerant is circulated through the second heat exchanger, and the compressor is operated at different stages of capacity at each time when a short-cycle time distribution is allocated, and the time distribution is determined. A refrigerating and air-conditioning system having a capacity control means for changing the average capacity in the short cycle by changing the amount of air generated on the high-pressure side or low-pressure side of the refrigerating cycle. A refrigeration / air-conditioning apparatus comprising a refrigerant container for reducing pressure fluctuation on a high pressure side or a low pressure side. 8. The refrigerating and air-conditioning apparatus according to claim 7, wherein a liquid receiver provided at an outlet of a heat exchanger operating as an oil separator or a condenser is used as the refrigerant container provided on the high pressure side. 9. The refrigerating and air-conditioning apparatus according to claim 7, wherein an accumulator provided on the suction side of the compressor is used as the refrigerant container provided on the low pressure side. 10. A refrigeration cycle in which refrigerant is circulated through a compressor, a first heat exchanger, a throttling means, and a second heat exchanger which can be operated with a stepwise capacity, and a short cycle time distribution. Operating the compressor at different stages of capacity at different times, and changing the time distribution to change the average capacity in the short cycle. Refrigeration characterized by providing a resistance element that adds flow resistance when a refrigerant flows on the side or the low-pressure side, and reducing high-pressure side or low-pressure side pressure fluctuation generated in the refrigeration cycle by operation of the compressor. Air conditioner. 11. The refrigerating and air-conditioning apparatus according to claim 10, wherein the resistance element provided on the high pressure side is a check valve provided on the discharge side of the compressor. 12. A refrigeration cycle in which refrigerant is circulated through a compressor, a first heat exchanger, a throttling means, and a second heat exchanger that can be operated with a stepwise capacity, and a short cycle time distribution. Operating the compressor at different stages of capacity at different times, and a capacity control means for changing the time distribution to change the average capacity in the short cycle. A refrigeration / air-conditioning apparatus comprising: a bypass circuit that bypasses a low-pressure side; and reduces a high-pressure side or a low-pressure side pressure fluctuation generated in the refrigeration cycle by operating the compressor. 13. The refrigeration / air-conditioning apparatus according to claim 12, wherein the bypass circuit is a circuit connecting a discharge side and a suction side of the compressor. 14. A compressor according to claim 12 or claim 13, wherein a control valve is provided in the bypass circuit, and the compressor operable with a stepwise capacity is provided with a different stage capacity at each time to which a short cycle time distribution is distributed. A refrigerating and air-conditioning system, wherein the control valve opens the bypass circuit when the compressor operates, and the control valve closes the bypass circuit when the compressor operates at a constant capacity. 15. The refrigeration / air-conditioning apparatus according to claim 12, wherein the bypass circuit is a circuit for returning the high-pressure liquid refrigerant condensed in the heat exchanger operating as a condenser of the refrigeration cycle to the compressor suction side. . 16. A pressure reducing means for reducing the pressure of a high-pressure liquid refrigerant in the bypass circuit,
A refrigeration / air-conditioning apparatus comprising a heat exchanger for exchanging heat between the refrigerant depressurized by the decompression means and the high-pressure liquid refrigerant condensed by the condenser. 17. The refrigeration / air-conditioning apparatus according to claim 12, wherein the bypass circuit is a circuit for returning oil separated by the oil separator to a low pressure side. 18. A refrigeration cycle in which a refrigerant can be circulated through a compressor, a first heat exchanger, a throttling means, and a second heat exchanger that can be operated in a stepwise capacity, and a short cycle time distribution. Operating the compressor at different stages of capacity in time, changing the time distribution to change the average capacity in the short cycle, and controlling the operating capacity of the compressor in the short cycle time distribution. A refrigerating air conditioner having a control valve for switching, wherein oil supply means for supplying oil to the control valve is provided. 19. An oil separator according to claim 18, wherein an oil separator is provided on the discharge side of the compressor, and the oil supply means supplies the oil separated by the oil separator or the refrigerant gas separated from the oil to the control valve. A refrigerating air conditioner, which is a supply circuit. 20. The oil supply device according to claim 18, wherein:
A refrigerating and air-conditioning apparatus, which is an oil supply circuit that supplies a gas refrigerant discharged from a compressor to a control valve. 21. A refrigeration cycle in which refrigerant is circulated through a compressor, a first heat exchanger, a throttling means, and a second heat exchanger operable with a stepwise capacity, and a short cycle time distribution. Operating the compressor at different stages of capacity in time, changing the time distribution to change the average capacity in the short cycle, and controlling the operating capacity of the compressor in the short cycle time distribution. A refrigeration / air-conditioning system having a switching control valve, wherein cooling means for cooling the control valve is provided. 22. The refrigerating and air-conditioning apparatus according to claim 21, wherein the cooling means is a refrigerant circuit for supplying a high-pressure liquid refrigerant condensed by a heat exchanger operating as a condenser of a refrigeration cycle to a control valve. . 23. The refrigeration / air-conditioning apparatus according to claim 21, wherein the cooling means is configured to cool the control valve by outside air around the refrigeration / air-conditioning apparatus. 24. A refrigeration cycle in which refrigerant is circulated through a compressor, a first heat exchanger, a throttling means, and a second heat exchanger that can be operated with a stepwise capacity, and a short cycle time distribution. Operating the compressor at different stages of capacity in time, changing the time distribution to change the average capacity in the short cycle, and opening and closing the flow path by moving a movable valve to perform the compression. In a refrigerating and air-conditioning system provided with a control valve for switching the operation capacity of the machine in the short-period time distribution, a portion of the control valve that comes into contact with the movable valve by movement of the movable valve or a portion of the movable valve that contacts the contact portion is subjected to an impact. A refrigeration / air-conditioning system characterized by comprising an impact mitigation means for alleviating the pressure. 25. The shock-absorbing means according to claim 24, wherein at least a part of the material of the movable valve which is in contact with the movable valve or which is in contact with the movable valve is made of a resin to reduce the impact. Refrigeration air conditioner characterized by the above-mentioned. 26. The shock absorbing means according to claim 24, wherein a speed reducing means for slowing down the movement of the movable valve is provided as the shock absorbing means, and the impact is reduced by reducing the speed at the time of contact by the movement of the movable valve. A refrigeration air conditioner characterized by the following. 27. A refrigeration cycle in which refrigerant is circulated through a compressor, a first heat exchanger, a throttling means, and a second heat exchanger operable in a stepwise capacity, and a short cycle time distribution. Operating the compressor at different stages of capacity at different times, and changing the time distribution to change the average capacity in the short cycle; and operating information of the refrigeration cycle during the operation in the short cycle or more. Measuring means for measuring a plurality of times within a predetermined time of the length, and controlling the refrigeration cycle including control by the capacity control means based on the obtained plurality of operation information. A refrigerating air conditioner characterized by the following. 28. A refrigeration cycle in which refrigerant is circulated through a compressor, a first heat exchanger, a throttling means, and a second heat exchanger that can be operated with a stepwise capacity, and a short cycle time distribution. Capacity control means for operating the compressor with different capacities over time and changing the time distribution to change the average capacity in the short cycle; and operating information of the refrigeration cycle during operation in a predetermined time within the short cycle. Measuring means for measuring time,
A refrigeration / air-conditioning apparatus, wherein the control of the refrigeration cycle including the control by the capacity control means is performed based on the obtained operation information. 29. The refrigeration cycle according to claim 5, wherein the refrigeration cycle includes at least a compressor operable at a stepwise capacity or a compressor operating at a constant capacity, separately from the compressor. A refrigeration and air-conditioning system comprising one unit.